There are many different styles of office chairs available both online and in retail stores, however most modern or new models are designed to be adjusted pneumatically. Chairs that feature a pneumatic height adjustment can simply be adjusted by pushing or pulling either a button or lever located right below the seat. With a little bit of pressure exerted by you while pushing or pulling the button or lever below the seat, you may easily have the chair's height go down. If you get off your chair and pull or push that same button or lever you can just as easily have the chair's height go up. Older office chair models can be adjusted by turning a thick bolt which allows you to pick the height you would like to have your chair positioned at. Adjusting the height of your chair may seem like common sense and a trivial matter, but it is actually very important to adjust the height to fit your body type. Chairs that are not properly adjusted to meet the needs of the user may cause back pain, eye strain from not being properly positioned in front of your computer screen, fatigue from poor circulation, and numerous other health issues. This can be especially true if you sit in the same position for long periods of time.
When determining the correct height to have your office chair at, first make sure to place it in front of the desk or work area you will be spending most of your time at. If you have a keyboard tray installed underneath your desk, you will also need to take that into consideration when deciding the correct height your office chair should be at. Keep in mind that you will want to have a good amount of clearance between your keyboard tray or desk and your thighs to enable you to work more comfortably. If your computer chair comes with arms you will also want to take that into consideration as well especially if they are not height adjustable.
Once you have determined where you will be spending most of your time sitting and ergonomic accessories that may also play a part in the height adjustment of your chair, you will want to locate where the button or lever is on your chair that controls the height. On most chair models, it is generally located on the right hand side of the chair right below the seat. Some higher end chairs may even have pictures on their levers explaining what each lever on the chair does. All chair models will vary, and you will need to take the time to understand what each button does in order to fully adjust your chair to meet your needs.
After you fully understand how to adjust your chair, place the chair in front of the work area in which you will be using it most often. If your chair can be adjusted pneumatically simply apply a little pressure and push down on the seat while pulling the lever up to have the chair go down in height. To have the chair go up, apply a little pressure to the bottom of the seat and pull up with one hand while simultaneously pulling the lever up with the other. Computer chairs that do not have a pneumatic lift can be adjusted by loosening the height adjustment bolt by hand and pulling up or pushing down on the seat until the desired height is reached. Once you are happy with the height of the chair you will then need to tighten the bolt back to its original place.
The most important part of this process is making sure to test the chair's height. Once you have reached the height you think your chair will work best for you at, take a seat to see how it feels. Your feet should be resting flat on the floor, with your knees bent at a ninety degree angle to optimize blood flow. It may take a few tries to get your chair positioned at the correct height, but keep in mind that it is important that you do to avoid unnecessary stress and pains. Some chairs will automatically lock into place once you have released the pneumatic height lever. Others may have a separate locking mechanism. If your chair requires a locking mechanism to lock the height in place, make sure to do so before putting your full weight on the chair.
With all office chairs, be sure to treat them with care. Raising and lowering your chair often may cause the chair to wear out quicker over time. If you do not share your chair with others, try to find your ideal height and keep it there, only adjusting it when necessary.
Thursday, February 17, 2011
Advances in Maintenance For Yokohama Fenders
Pneumatic fenders are essential for preventing damage between ships, or between ships and wharves. Yokohama has been a leader in the field for so long that the term "Yokohama Fender" has become synonymous with pneumatic fenders in general. The company currently dominates the field with a full 80% of all the pneumatic fenders being manufactured today.
Though pneumatic fenders are sturdy and adaptable to many situations and circumstances, they are not indestructible and do require periodic maintenance. In the past, this typically involved lifting them completely out of the water for inspection and a check of their inflation pressure. Obviously, this cuts into the efficiency of an entire wharf or dock operation when pneumatic fenders are taken out of commission completely for maintenance.
Yokohama recently announced a system that can monitor air pressure by remote sensing (a system adapted from their Air Watch setup for automotive tires). Dubbed the Fender Watch system, it entails a sensor on a metal fitting, set inside a Yokohama fender. Via a wireless signal, the sensor sends inflation data to the handheld terminals of maintenance personnel. With this system, maintenance can get accurate readings on the fender's inflation at distances up to 30 meters. This remote pressure sensing can also help monitor and regulate the distance between two vessels during ship-to-ship transfers of crude oil or liquefied petroleum gas.
Since pneumatic fenders are typically used in batteries of four or more, Yokohama's Fender Watch system can take readings from up to four fenders simultaneously. The sensors are also equipped to send alarm signals should the inflation pressure move significantly above or below the desired settings set by the users.
Though pneumatic fenders are sturdy and adaptable to many situations and circumstances, they are not indestructible and do require periodic maintenance. In the past, this typically involved lifting them completely out of the water for inspection and a check of their inflation pressure. Obviously, this cuts into the efficiency of an entire wharf or dock operation when pneumatic fenders are taken out of commission completely for maintenance.
Yokohama recently announced a system that can monitor air pressure by remote sensing (a system adapted from their Air Watch setup for automotive tires). Dubbed the Fender Watch system, it entails a sensor on a metal fitting, set inside a Yokohama fender. Via a wireless signal, the sensor sends inflation data to the handheld terminals of maintenance personnel. With this system, maintenance can get accurate readings on the fender's inflation at distances up to 30 meters. This remote pressure sensing can also help monitor and regulate the distance between two vessels during ship-to-ship transfers of crude oil or liquefied petroleum gas.
Since pneumatic fenders are typically used in batteries of four or more, Yokohama's Fender Watch system can take readings from up to four fenders simultaneously. The sensors are also equipped to send alarm signals should the inflation pressure move significantly above or below the desired settings set by the users.
Fitting Tyres Correctly and Quickly With Wheel Balancers
It is very important that tyres are balanced correctly. If wheels are not balanced it can cause vibration and make the vehicle uncomfortable to drive. This can also cause wear in the suspension, meaning more expensive visits to the garage. The first signs of incorrect balance is the steering wobbles on the car when driving at speed.
The best way to do this correctly is to use a wheel balancer machine. The machine rotates the tyre and wheel assembly and automatically calculates the weight and location of the balance counter weight. There are many types of machine out there suited for different purposes.
Smaller machines are suitable for smaller cars and motorcycles. These are controlled by hand spin and are suitable for bike shops for a low cost solution. There are slightly more advanced machines that rotate automatically at hand speed, so there is no need for a guard and is more compact for those with little space.
The more expensive and advanced machines are all automated. Pre-programmed weights can be selected so the wheel is automatically balanced perfectly. These are more suited to tyre shops. These wheel balancers can be even more advanced with colour VDU displays and printers to show results. Some of these have a weight placement arm for better control and testing.
Of course there are even bigger machines that are for heavy goods vehicles. Only specialised tyre fitters usually have these for commercial vehicles. They have pneumatic lifts for raising the shaft height, so it is not only easier but safer.
The best way to do this correctly is to use a wheel balancer machine. The machine rotates the tyre and wheel assembly and automatically calculates the weight and location of the balance counter weight. There are many types of machine out there suited for different purposes.
Smaller machines are suitable for smaller cars and motorcycles. These are controlled by hand spin and are suitable for bike shops for a low cost solution. There are slightly more advanced machines that rotate automatically at hand speed, so there is no need for a guard and is more compact for those with little space.
The more expensive and advanced machines are all automated. Pre-programmed weights can be selected so the wheel is automatically balanced perfectly. These are more suited to tyre shops. These wheel balancers can be even more advanced with colour VDU displays and printers to show results. Some of these have a weight placement arm for better control and testing.
Of course there are even bigger machines that are for heavy goods vehicles. Only specialised tyre fitters usually have these for commercial vehicles. They have pneumatic lifts for raising the shaft height, so it is not only easier but safer.
Smart Tips to Use Pneumatic Floor Stapler
When talking about wood-flooring, you will find that it uses a tongue-and-groove system to lay the flooring. The system will mill the wood-flooring into the sides of the boards. In order give a tight fit, a tongue will be set to fit the groove. In this matter, the use of pneumatic floor stapler is very important. This is a type of tool that is designed for the tongue-and-groove flooring installation. You will find that the mallet is used to trigger the shooting of the staple. This will drive the boards tightly get together when the staple is shot. When you are about to use this tool, you can follow the following steps.
1. You should lay the first board. In this matter, you have to make sure that the grooved side faces the wall. Also you have to make sure that you make 3/8-inch expansion gap from it. You will find that this expansion gap will allow the board to make movement when the climate changes. But next, you will find that this will be covered up by the floor trim. When you are sure about those things, you can nail down the first board with your nail gun by shooting pairs of nails to the face of the board.
2. You should lay the next boards. For this, you should connect the ends of the boards. You should cut the final pieces on your miter saw at the walls as you need. Then, you should continue the process for the next few courses. In this step, you should connect them by their tongue-and-groove sides. You should also do the top-nailing as the previous step. You have to do this until you have enough courses so that you can sit the pneumatic floor stapler. For this, you might need four or five courses.
3. The next thing that you should do is that you should hook the stapler that you will use up to the air tank. Alongside the previous boards that you have installed, you should set the board of the next course. Make sure that it is in its place correctly. On the top installed courses, you should sit the stapler. Make sure that its nose hook down over the new board that you will install.
4. Gently, knock the stapler against that floorboard. For this, you can use the mallet that you have. After that, you should swing it fully so that it hits the rubber firing pad of the stapler.
5. Then, you should do that in every foot on the board. Make sure that you staple the board perfectly. When you have finished with this process, you can use your miter saw for cutting the end of pieces of the board when it is needed.
6. Finally, you should it across the floor with the pneumatic stapler until you are close to the opposing wall or you find that there is no longer enough room to fully swing the mallet. Lay the last few courses with your nail gun, as you did the first few courses.
1. You should lay the first board. In this matter, you have to make sure that the grooved side faces the wall. Also you have to make sure that you make 3/8-inch expansion gap from it. You will find that this expansion gap will allow the board to make movement when the climate changes. But next, you will find that this will be covered up by the floor trim. When you are sure about those things, you can nail down the first board with your nail gun by shooting pairs of nails to the face of the board.
2. You should lay the next boards. For this, you should connect the ends of the boards. You should cut the final pieces on your miter saw at the walls as you need. Then, you should continue the process for the next few courses. In this step, you should connect them by their tongue-and-groove sides. You should also do the top-nailing as the previous step. You have to do this until you have enough courses so that you can sit the pneumatic floor stapler. For this, you might need four or five courses.
3. The next thing that you should do is that you should hook the stapler that you will use up to the air tank. Alongside the previous boards that you have installed, you should set the board of the next course. Make sure that it is in its place correctly. On the top installed courses, you should sit the stapler. Make sure that its nose hook down over the new board that you will install.
4. Gently, knock the stapler against that floorboard. For this, you can use the mallet that you have. After that, you should swing it fully so that it hits the rubber firing pad of the stapler.
5. Then, you should do that in every foot on the board. Make sure that you staple the board perfectly. When you have finished with this process, you can use your miter saw for cutting the end of pieces of the board when it is needed.
6. Finally, you should it across the floor with the pneumatic stapler until you are close to the opposing wall or you find that there is no longer enough room to fully swing the mallet. Lay the last few courses with your nail gun, as you did the first few courses.
How to Use Pneumatic Tools Safely in the Workplace
For craftsmen, carpenters, and cabinet shops, a quality pneumatic brad nailer is basically a bare necessity. Designed for trim, baseboards, cabinets, furniture, and etc, a brad nailer is built for the most precise, clean, and effective nailing. Where-ever you need smooth and crafty fabrication or installation, a brad nailer is just the tool for the job. Finding the best brad nailer, though, can be a tough process, so I've compiled a bit of information on the industry's very best pneumatic brad nailers to help you narrow your search for the ultimate air tool.
Firstly, Senco is known for building some of the best pneumatic tools this industry has ever seen and their FinsihPro18 (18 gauge) brad nailer is brilliant example of the Senco difference. With the power, durability, and perfectly compact design to bring you the most professional, impressive results, the FinishPro 18 is a tool to be remembered. Weighing only 2.9 lbs the tool's lightweight design entirely eliminates the pains of continuous or overhead work, and this comfort comes without any sacrifice to power; the nailer drives fasteners up to 2" into hard woods making this brad nailer ideal for cabinetry, trim, and any type of finish work. The tool also has an adjustable depth-of-drive for the most precise nailing, and a hardened steel driver for longevity and durability. The tool is simple to load, and with a low-load indicator you'll never be caught off guard with an empty magazine. The tool's no mar pad and rear exhaust (designed to keep debris and oils away from your materials) work together to ensure your workpieces are always clean and unsmudged. Ultimately, this nailer is tough enough for heavy-duty applications while being ultra compact to ensure you are always comfortable and in control of each shot and each application. Additionally, as the Finish Pro 18 only costs around $80 - $90, this brilliant tool comes at a brilliantly affordable price.
On another hand, Porter-Cable's BN200B is another (18 gauge) brad nailer with all the power and innovation to bring you impressive results with every single shot. With a long-lasting, virtually maintenance-free motor, the tool's durable high-performance is unfailingly reliable, and with a rear exhaust keeping oils and contaminants away from your workpieces, your results are clean and precise. Additionally, a (removable) no-marring nose piece keeps your materials protected against scrapes and scuffs for for the cleanest possible results. The BN200B drives nails from 5/8" to 2" in length (with a depth-of-drive adjustment), and because of an internal piston catch, the tool delivers consistent max power through every shot. A low nail reload mechanism indicates when a reload is required, and with a tool-free jam release, nail removal is always simple. The tool has a 100 nail magazine capacity, and weighing only 2.6 lbs the tool is comfortable during continuous use and even the most awkward applications. Although its strikingly lightweight, the tool is also built with a strong die-cast aluminum body for long-lasting durability, and a special hardened driver blade additionally contributes to the tool's overall longevity. Ultimately, this nailer is pretty awesome, and pricing at only around $100, its a superior tool that will also fit into your budget.
Firstly, Senco is known for building some of the best pneumatic tools this industry has ever seen and their FinsihPro18 (18 gauge) brad nailer is brilliant example of the Senco difference. With the power, durability, and perfectly compact design to bring you the most professional, impressive results, the FinishPro 18 is a tool to be remembered. Weighing only 2.9 lbs the tool's lightweight design entirely eliminates the pains of continuous or overhead work, and this comfort comes without any sacrifice to power; the nailer drives fasteners up to 2" into hard woods making this brad nailer ideal for cabinetry, trim, and any type of finish work. The tool also has an adjustable depth-of-drive for the most precise nailing, and a hardened steel driver for longevity and durability. The tool is simple to load, and with a low-load indicator you'll never be caught off guard with an empty magazine. The tool's no mar pad and rear exhaust (designed to keep debris and oils away from your materials) work together to ensure your workpieces are always clean and unsmudged. Ultimately, this nailer is tough enough for heavy-duty applications while being ultra compact to ensure you are always comfortable and in control of each shot and each application. Additionally, as the Finish Pro 18 only costs around $80 - $90, this brilliant tool comes at a brilliantly affordable price.
On another hand, Porter-Cable's BN200B is another (18 gauge) brad nailer with all the power and innovation to bring you impressive results with every single shot. With a long-lasting, virtually maintenance-free motor, the tool's durable high-performance is unfailingly reliable, and with a rear exhaust keeping oils and contaminants away from your workpieces, your results are clean and precise. Additionally, a (removable) no-marring nose piece keeps your materials protected against scrapes and scuffs for for the cleanest possible results. The BN200B drives nails from 5/8" to 2" in length (with a depth-of-drive adjustment), and because of an internal piston catch, the tool delivers consistent max power through every shot. A low nail reload mechanism indicates when a reload is required, and with a tool-free jam release, nail removal is always simple. The tool has a 100 nail magazine capacity, and weighing only 2.6 lbs the tool is comfortable during continuous use and even the most awkward applications. Although its strikingly lightweight, the tool is also built with a strong die-cast aluminum body for long-lasting durability, and a special hardened driver blade additionally contributes to the tool's overall longevity. Ultimately, this nailer is pretty awesome, and pricing at only around $100, its a superior tool that will also fit into your budget.
Pneumatic Equipments For All Your DIY Constructions at Home
Pneumatic equipments, or air tools, are tools or equipments that use gas or compressed air to utilize the tools. Some of these tools are also using CO2 or carbon dioxide, usually stored in a small cylinder, for convenient portability. These tools are commonly used in different industrial operations, especially for applications where electric or other motors are not applicable due to safety and protections. These tools are required and essential in all construction and manufacturing operations. For whatever kind of Do-It-Yourself operations you have, you will surely find a pneumatic tool that you can use.
Most industrial operators prefer to use pneumatic tools instead of electric or battery-powered equipments because these tools are easy to use, more accurate, light-weight, less expensive, durable, and provide more power and torque when in use. Use of these equipments does not require the help of professional operators because these are usually user-friendly and easy to operate.
Pneumatic equipments are usually used in moving heavy loads from one location to another, especially in areas and situations where forklifts and cranes are not possible to be used. With the help of these pneumatic equipment and tools, your tasks and your operations will turn out successful and a lot easier. Maintenance is only in a minimum requirement since these kinds of tools rarely experience overheating because air is always present to cool them down. There are just some considerations when using these equipments. The tools should properly match the air compressor for better results and lesser occurrences of damages. The air hose should also fit the tools and the compressor. And the air pressure should be correctly adjusted according to the tools.
Purchasing pneumatic tools that you need for construction or just for any DIY purposes, you can find great deals from suppliers as the competition in sales and marketing for these tools are really growing. However, you would not definitely want to get just anything that is there. You would surely look for the best pneumatic equipments at affordable prices there could be. Finding the right pneumatic tools that have the quality and durability will ensure that what you paid for the equipments are really worthwhile.
Before you buy, search for the right supplier who does not only provide quality equipments but also gives importance to complete customer services for customers' satisfaction. Some of them also provide training or initial guide for first time users and delivery and other after-sales services needed.
Repairs and maintenance may also be provided by the supplier. But to ensure you get all these services at low expenses but high on satisfaction, choose the right supplier. The company should have such skilled and knowledgeable manpower to be able to handle all the necessary and proper services you might need regarding the supply of the right kinds of pneumatic tools, including the services for repair and maintenance in case your equipments malfunction.
Most industrial operators prefer to use pneumatic tools instead of electric or battery-powered equipments because these tools are easy to use, more accurate, light-weight, less expensive, durable, and provide more power and torque when in use. Use of these equipments does not require the help of professional operators because these are usually user-friendly and easy to operate.
Pneumatic equipments are usually used in moving heavy loads from one location to another, especially in areas and situations where forklifts and cranes are not possible to be used. With the help of these pneumatic equipment and tools, your tasks and your operations will turn out successful and a lot easier. Maintenance is only in a minimum requirement since these kinds of tools rarely experience overheating because air is always present to cool them down. There are just some considerations when using these equipments. The tools should properly match the air compressor for better results and lesser occurrences of damages. The air hose should also fit the tools and the compressor. And the air pressure should be correctly adjusted according to the tools.
Purchasing pneumatic tools that you need for construction or just for any DIY purposes, you can find great deals from suppliers as the competition in sales and marketing for these tools are really growing. However, you would not definitely want to get just anything that is there. You would surely look for the best pneumatic equipments at affordable prices there could be. Finding the right pneumatic tools that have the quality and durability will ensure that what you paid for the equipments are really worthwhile.
Before you buy, search for the right supplier who does not only provide quality equipments but also gives importance to complete customer services for customers' satisfaction. Some of them also provide training or initial guide for first time users and delivery and other after-sales services needed.
Repairs and maintenance may also be provided by the supplier. But to ensure you get all these services at low expenses but high on satisfaction, choose the right supplier. The company should have such skilled and knowledgeable manpower to be able to handle all the necessary and proper services you might need regarding the supply of the right kinds of pneumatic tools, including the services for repair and maintenance in case your equipments malfunction.
Pneumatics and Control Valves Part 2
Air compressors are often called a hidden utility because not many people know about air compressors. The closest they get to an air compressor is the buzzing of air wrenches when they get their tires fitted. There are a myriad of pneumatic tools available on the market today. Cabinet and furniture shops use pneumatic nail guns and staplers, because nothing else compares to the speed and reliability of these tools. Blow off guns are the most common use for compressed air. From blowing off chips in a machine shop to a makeshift air brooms, these guns are extremely convenient tools. A blow off gun is simply a push button valve with a discharge valve to focus the escaping air. This type of gun is preferred when operators are restricted to specific machines, such as lathes, mills and punch presses.
Pneumatic energy is regulated and controlled by pneumatic valves. Functionally, valves are divided into four major groups viz, direction control, flow control, pressure control and non-return and special type valves. As per construction, valves are sub-grouped as seat valves and sliding or spool valves. However, spool valves are easier to manufacture. Valves are actuated in various methods, viz, manually, mechanically, electrically, pneumatically and by various combined mode of actuation. Specially designed valves like quick exhaust, time delay and shuttle and twin pressure valves are used to impart various functions to pneumatic circuits.
To control the to and fro motion of a pneumatic cylinder, the air energy needs to be regulated, controlled and reversed with a pre determined sequence in a pneumatic system. Similarly, one may have to control the quantity of pressure and flow rate to generate the desired level of force and speed of actuators. To achieve these functions valves are used. Valves are fluid power elements used for controlling and regulating the working medium, i.e, the compressed air in the case of a pneumatic system.
Board valves are used to start and stop pneumatic energy, control the direction of flow of compressed air, control the flow rate of compressed air and control the pressure rating of the compressed air. Direction control valves are mainly used to direct the flow of pressure fluid in the desired direction. They can be actuated to assume different positions by various actuating mediums. This results in corresponding connection or disruption of flow between various port openings. Direction control valves have two, three, four or five ports or openings.
In a direction control valve, the force is applied directly on the working piston or spool. The control method could be manual, mechanical, pneumatic, magnetic or a combination of any two. Magnets are commonly used for actuation of pneumatic valves. When the magnet is excited, the plunger gets attracted to it and it presses down on the valve spool. The pneumatic method acts on a spool or piston with a large area which in turn transfers the actuating force to the spool. Mechanical method involves the use of rollers, springs and other mechanical elements are used to actuate the valve. In the manual method the angular movement of a pedal or lever is transmitted to the spool.
Pneumatic energy is regulated and controlled by pneumatic valves. Functionally, valves are divided into four major groups viz, direction control, flow control, pressure control and non-return and special type valves. As per construction, valves are sub-grouped as seat valves and sliding or spool valves. However, spool valves are easier to manufacture. Valves are actuated in various methods, viz, manually, mechanically, electrically, pneumatically and by various combined mode of actuation. Specially designed valves like quick exhaust, time delay and shuttle and twin pressure valves are used to impart various functions to pneumatic circuits.
To control the to and fro motion of a pneumatic cylinder, the air energy needs to be regulated, controlled and reversed with a pre determined sequence in a pneumatic system. Similarly, one may have to control the quantity of pressure and flow rate to generate the desired level of force and speed of actuators. To achieve these functions valves are used. Valves are fluid power elements used for controlling and regulating the working medium, i.e, the compressed air in the case of a pneumatic system.
Board valves are used to start and stop pneumatic energy, control the direction of flow of compressed air, control the flow rate of compressed air and control the pressure rating of the compressed air. Direction control valves are mainly used to direct the flow of pressure fluid in the desired direction. They can be actuated to assume different positions by various actuating mediums. This results in corresponding connection or disruption of flow between various port openings. Direction control valves have two, three, four or five ports or openings.
In a direction control valve, the force is applied directly on the working piston or spool. The control method could be manual, mechanical, pneumatic, magnetic or a combination of any two. Magnets are commonly used for actuation of pneumatic valves. When the magnet is excited, the plunger gets attracted to it and it presses down on the valve spool. The pneumatic method acts on a spool or piston with a large area which in turn transfers the actuating force to the spool. Mechanical method involves the use of rollers, springs and other mechanical elements are used to actuate the valve. In the manual method the angular movement of a pedal or lever is transmitted to the spool.
Do Not Overlook Central Pneumatic Air Tools
Central pneumatic air tools have quite a bit to offer in terms of durability, efficiency, pricing, and variety. If you look to these options when buying air tools you should be able to find what you are looking for, and hopefully much more. There are many companies that offer these types of tools, but you need to find one that also has what you need in terms of parts and accessories. This is why buying Central pneumatic air tools is such a good idea - you get access to a large lineup of everything you could possibly need.
The type of Central pneumatic parts that you need in the future may not be the same as you do right now. For instance, if you just purchased a pneumatic air compressor there is no reason to believe that you should have to go out and buy any additional parts. But in the near future, maybe when you are completing a particular job, you may find that adding a new part to your tool is something that you have to do. As long as you have access to what you want and need nothing should be standing in your way from getting the job done.
One of the reasons why Central pneumatic air tools are so popular is the price. When you are in the market for tools you probably have two things in mind: price and effectiveness. In other words, you want to save money but not if you have to give up anything in terms of getting the job done. This is where Central pneumatic tools really thrive. You can rest assured that everything you buy is going to fit your needs from a money perspective, while also offering just what you have been looking for in terms of effectiveness and reliability. It goes without saying that you cannot have one without the other.
With the right tools and parts you can build many items, like a pneumatic air cannon for instance. There are plans available for building these, and if you have the parts in place you should be able to put everything together and end up with the cannon that you set out to build. For many, building things like a pneumatic air cannon is a fun project.
When shopping for Central pneumatic air tools you will come across everything from drill-screw drivers to accessories and much more. You should have some idea of what you are looking for before you start perusing the many tools that are on the market. This makes it simpler to not only buy what you want, but to do so without wasting time and valuable resources.
The type of Central pneumatic parts that you need in the future may not be the same as you do right now. For instance, if you just purchased a pneumatic air compressor there is no reason to believe that you should have to go out and buy any additional parts. But in the near future, maybe when you are completing a particular job, you may find that adding a new part to your tool is something that you have to do. As long as you have access to what you want and need nothing should be standing in your way from getting the job done.
One of the reasons why Central pneumatic air tools are so popular is the price. When you are in the market for tools you probably have two things in mind: price and effectiveness. In other words, you want to save money but not if you have to give up anything in terms of getting the job done. This is where Central pneumatic tools really thrive. You can rest assured that everything you buy is going to fit your needs from a money perspective, while also offering just what you have been looking for in terms of effectiveness and reliability. It goes without saying that you cannot have one without the other.
With the right tools and parts you can build many items, like a pneumatic air cannon for instance. There are plans available for building these, and if you have the parts in place you should be able to put everything together and end up with the cannon that you set out to build. For many, building things like a pneumatic air cannon is a fun project.
When shopping for Central pneumatic air tools you will come across everything from drill-screw drivers to accessories and much more. You should have some idea of what you are looking for before you start perusing the many tools that are on the market. This makes it simpler to not only buy what you want, but to do so without wasting time and valuable resources.
How Pneumatic Tools Work
Pneumatic tool use is quickly becoming the most affordable and efficient way to work on projects around the home and in the shop. When it is time to work on your home improvement projects there are many reasons to choose hand held pneumatic tools. UK suppliers are available to provide you with all the necessary products and accessories to make your home projects go as smoothly as possible.
Pneumatic means "contains air" and that is exactly what is powering your equipment. These are designed to make your work easier and eliminate the hard work that is required to drive nails, turn screws and a variety of other tasks. They are affordable and provide the user with professional results in all of their projects.
The air compressor you will use is the source of power for your pneumatic tools. It is also the biggest investment that you will make in your equipment box. There is a wide variety of air compressors available to power your hand held pneumatic products. UK suppliers of these compressors will give you a choice of size, air pressure and air flow capacities on their selection of compressors. It is important that you choose the right one to accommodate your pneumatic equipment.
There are a number of attachments you can include with your collection of pneumatic tools. These types will run much cooler than their electrical counterparts because it is air that is the source of energy. Some attachments to consider include the blow gun for such jobs as blowing away dust and dirt, a nail gun for ease in driving nails, a spray paint gun, air stapler, air sander, and caulking gun. All of these can be powered with the use of air and an air compressor.
Pneumatic tools will last for many years if they are properly maintained as there are few moving parts. UK suppliers will tell you that this is the reason why they are almost indestructible. Keep them well lubricated and properly cleaned and you will have and enjoy them for many years.
It is also important to note that you must use safety precautions when using your pneumatic product. Wear the proper safety equipment to keep you safe during operation. Read the instructions that come with them carefully to ensure that you are taking the proper safety precautions. For some of these, there is a great deal of air pressure and a serious injury could occur if you are not following proper safety guidelines.
When choosing the pneumatic tools you require, make sure that you are considering your needs for the project as well as the running time for the compressor. There are experts available that will be able to help you determine what your needs are and which will fit your requirements best.
Pneumatic means "contains air" and that is exactly what is powering your equipment. These are designed to make your work easier and eliminate the hard work that is required to drive nails, turn screws and a variety of other tasks. They are affordable and provide the user with professional results in all of their projects.
The air compressor you will use is the source of power for your pneumatic tools. It is also the biggest investment that you will make in your equipment box. There is a wide variety of air compressors available to power your hand held pneumatic products. UK suppliers of these compressors will give you a choice of size, air pressure and air flow capacities on their selection of compressors. It is important that you choose the right one to accommodate your pneumatic equipment.
There are a number of attachments you can include with your collection of pneumatic tools. These types will run much cooler than their electrical counterparts because it is air that is the source of energy. Some attachments to consider include the blow gun for such jobs as blowing away dust and dirt, a nail gun for ease in driving nails, a spray paint gun, air stapler, air sander, and caulking gun. All of these can be powered with the use of air and an air compressor.
Pneumatic tools will last for many years if they are properly maintained as there are few moving parts. UK suppliers will tell you that this is the reason why they are almost indestructible. Keep them well lubricated and properly cleaned and you will have and enjoy them for many years.
It is also important to note that you must use safety precautions when using your pneumatic product. Wear the proper safety equipment to keep you safe during operation. Read the instructions that come with them carefully to ensure that you are taking the proper safety precautions. For some of these, there is a great deal of air pressure and a serious injury could occur if you are not following proper safety guidelines.
When choosing the pneumatic tools you require, make sure that you are considering your needs for the project as well as the running time for the compressor. There are experts available that will be able to help you determine what your needs are and which will fit your requirements best.
Counterbalance apparatus with transverse pneumatic spring and bellcrank linkage
Articles known as pneumatic or gas springs, which for convenience can be referred to as counterbalance links have become common in commercial articles, particularly in the automotive industry, but they are being used in many other fields whereverthe need is present to provide a counterbalance force for closure units, such as lids, doors and cabinet fronts, and gas spring replacement for mechanical spring fittings has become prevalent. In some fields of use, particularly in the automotive fieldwhere pneumatic springs are used on each side of trunk lids and hatch backs, the springs counterbalance the weight of the lid or hatch back. The gas springs are retracted, i.e., the spring piston rod is moved into the spring cylinder, when the lids areclosed.
Then the gas spring units can extend, under gas pressure force acting on the effective piston shaft cross-section area, to move the lid to an open position. As is true of many gas springs, a control orifice by-pass in the gas spring,effectively slows the opening speed of the lid.
In the automotive field, particularly where pneumatic springs are used on hoods, trunk lids and hatch backs, two springs are used, primarily to provide balanced spaced apart forces to counterbalance the weight of the closure and prevent twistingor warping of the closure unit relative to its hinge axis. This invention while developed relative to automotive uses is not restricted to such field. It results in a compact installation using a single pneumatic spring connected through bell cranksand idler links to a hinged closure member. The elongate spring is mounted on and between bellcranks with the spring floating, between positions, in a direction transverse to the hinge axis of the closure. In conjunction with the counterbalanceapparatus the pneumatic spring construction has been improved to provide a desired multi-output force feature as well as incorporating a unique method and structure to effectively decrease loss of operative gas pressure within the pneumatic springresulting primarily from leakage of the gas directly through the shaft seal due to permeability of the material from which the seal is made. The latter aspect can be referred to as permeability compensation or pressure decay compensation.
Examples of transverse springs with bellcrank linkage are seen in the following U.S. Patents: U.S. Pat. No. 3,724,797 to H Freitaz et al for Resilient Seat; U.S. Pat. No. 4,416,094 to F. Bugener et al for Attic Window Assembly; and U.S. Pat. No. Re. 26,162 to A. K. Simons et al for Vehicle Seat Rebound Control. An example of a different dual output force concept in a pneumatic spring can be seen in applicant's U.S. Pat. No. 4,451,964 (also U.S. Pat. No. 4,451,978) where afloating piston is utilized to provide the dual output force. While not teaching the pressure decay compensation invention of this application, U.S. Pat. No. 4,408,751 to Daniel P. Dodson and George C. Ludwig for Multi-chamber Temperature CompensatedPneumatic Counterbalance shows a fixed partition or wall module providing a separate gas chamber in a pneumatic counterbalance cylinder.
A transversely mounted single pneumatic spring, bell crank and idler link assembly or apparatus will provide a compact installation for hinged closures such as automobile trunk lids or doors and other similar closures.
The spring will float,being attached only to spaced-apart bellcranks. In an automobile trunk installation, where the trunk lid is mounted by hinges or "goosenecks" between each side of the lid and automobile frame, the forward space required for this counterbalance assemblyis minimized being installed laterally just behind the rear seat and in the forward upper portion of the trunk. Only one spring unit is required, thus minimizing cost. The spring unit is effectively hidden or concealed at the front upper part of thetrunk minimizing damage by items placed in the trunk. Other pneumatic spring enhancements, such as the multi-output force feature of the present invention and the pressure decay compensation feature of the present invention can be incorporated in thespring unit to provide convenient operation of opening the lid and to improve the life expectancy of the pneumatic spring by minimizing and effectively negating pressure loss due to leakage of gas past the shaft seal. If desired, other features such astemperature compensation as taught in U.S. Pat. No. 4,408,751 can be easily added to the pneumatic spring inasmuch as the spring cylinder length can be made substantially longer than the piston shaft, the stroke of which is relatively short. Excesscylinder length provides the space or volume zones used for the various, above mentioned, enhancement features.
The present invention has for a primary object the provision of a compact counterbalance apparatus for use with closure units where a single elongate pneumatic spring having shaft and cylinder end connector links are connected to arms of twospaced apart bellcranks, the other arms of which connect with idler links to a closure unit, secured for hinged movement to the frame structure of the closure, e.g., an autombile trunk lid with associated vehicle frame structure, the spring beingsupported laterally on the bellcranks so it floats in a plane parallel with the hinge axis of the closure lid.
Additional novel objects reside in the provision of improvements in the pneumatic springs which can be used with the aforementioned transverse spring and bell-crank apparatus to (1) provide a dual or multiple output force for the spring shaftseal to vary the volume and, of prime importance, changing the effective cross-section area of the piston shaft of the spring cylinder near the end of the compression stroke, and (2) to provide a special extra volume chamber in the spring cylinder with asealed partition wall between the extra chamber and the operative volume part of the spring cylinder and having an auxiliary supply of gas under higher pressure than that of the spring operative gas pressures and with the spring shaft seal and thepartition wall seal made from specific material so that gas permeability characteristics of both seals are as desired to compensate for various conditions which cause leakage from the cylinder. As desired, the gas spring used in the counterbalanceapparatus can be used with or without any or all of the above noted enhancements to this spring operation.
In conjunction with the foregoing improvement in the dual or multiple force output provisions of the pneumatic spring unit, further objects reside in providing such a spring for substantially vertical disposition filled with a predeterminedquantity of oil or the like to enable operation as a liquid pneumatic shock absorber with plural output forces enabled by controlled movement of the shaft to cylinder sealing assembly near the retraction limit position of the shaft. Another object inconnection herewith resides in the incorporation of a supplemental disc valve unit which is located near the closed end of the spring cylinder and is provided with an orifice bleed to enable controlled movement, at least in the rebound direction ofmovement of the counterbalance unit when the shaft is retracted to the higher output force position. The disc valve can be fixed with a small axial floating movement to shift from an effective sealed relationship of its periphery with the cylinder wallto a free flow relationship so that orifice controlled flow is only in the direction of shaft extension under the high output force. The disc can be fixed in the cylinder wall to provide orifice controlled flow in both directions if so desired.
The invention may be embodied in other specific forms without departing from the spirit or essential characteristics thereof. The present embodiments are therefore to be considered in all respects as illustrative and not restrictive, the scopeof the invention being indicated by the appended claims rather than by the foregoing description, and all changes which come within the meaning and rage of equivalency of the claims are therefore intended to be embraced therein.
Then the gas spring units can extend, under gas pressure force acting on the effective piston shaft cross-section area, to move the lid to an open position. As is true of many gas springs, a control orifice by-pass in the gas spring,effectively slows the opening speed of the lid.
In the automotive field, particularly where pneumatic springs are used on hoods, trunk lids and hatch backs, two springs are used, primarily to provide balanced spaced apart forces to counterbalance the weight of the closure and prevent twistingor warping of the closure unit relative to its hinge axis. This invention while developed relative to automotive uses is not restricted to such field. It results in a compact installation using a single pneumatic spring connected through bell cranksand idler links to a hinged closure member. The elongate spring is mounted on and between bellcranks with the spring floating, between positions, in a direction transverse to the hinge axis of the closure. In conjunction with the counterbalanceapparatus the pneumatic spring construction has been improved to provide a desired multi-output force feature as well as incorporating a unique method and structure to effectively decrease loss of operative gas pressure within the pneumatic springresulting primarily from leakage of the gas directly through the shaft seal due to permeability of the material from which the seal is made. The latter aspect can be referred to as permeability compensation or pressure decay compensation.
Examples of transverse springs with bellcrank linkage are seen in the following U.S. Patents: U.S. Pat. No. 3,724,797 to H Freitaz et al for Resilient Seat; U.S. Pat. No. 4,416,094 to F. Bugener et al for Attic Window Assembly; and U.S. Pat. No. Re. 26,162 to A. K. Simons et al for Vehicle Seat Rebound Control. An example of a different dual output force concept in a pneumatic spring can be seen in applicant's U.S. Pat. No. 4,451,964 (also U.S. Pat. No. 4,451,978) where afloating piston is utilized to provide the dual output force. While not teaching the pressure decay compensation invention of this application, U.S. Pat. No. 4,408,751 to Daniel P. Dodson and George C. Ludwig for Multi-chamber Temperature CompensatedPneumatic Counterbalance shows a fixed partition or wall module providing a separate gas chamber in a pneumatic counterbalance cylinder.
A transversely mounted single pneumatic spring, bell crank and idler link assembly or apparatus will provide a compact installation for hinged closures such as automobile trunk lids or doors and other similar closures.
The spring will float,being attached only to spaced-apart bellcranks. In an automobile trunk installation, where the trunk lid is mounted by hinges or "goosenecks" between each side of the lid and automobile frame, the forward space required for this counterbalance assemblyis minimized being installed laterally just behind the rear seat and in the forward upper portion of the trunk. Only one spring unit is required, thus minimizing cost. The spring unit is effectively hidden or concealed at the front upper part of thetrunk minimizing damage by items placed in the trunk. Other pneumatic spring enhancements, such as the multi-output force feature of the present invention and the pressure decay compensation feature of the present invention can be incorporated in thespring unit to provide convenient operation of opening the lid and to improve the life expectancy of the pneumatic spring by minimizing and effectively negating pressure loss due to leakage of gas past the shaft seal. If desired, other features such astemperature compensation as taught in U.S. Pat. No. 4,408,751 can be easily added to the pneumatic spring inasmuch as the spring cylinder length can be made substantially longer than the piston shaft, the stroke of which is relatively short. Excesscylinder length provides the space or volume zones used for the various, above mentioned, enhancement features.
The present invention has for a primary object the provision of a compact counterbalance apparatus for use with closure units where a single elongate pneumatic spring having shaft and cylinder end connector links are connected to arms of twospaced apart bellcranks, the other arms of which connect with idler links to a closure unit, secured for hinged movement to the frame structure of the closure, e.g., an autombile trunk lid with associated vehicle frame structure, the spring beingsupported laterally on the bellcranks so it floats in a plane parallel with the hinge axis of the closure lid.
Additional novel objects reside in the provision of improvements in the pneumatic springs which can be used with the aforementioned transverse spring and bell-crank apparatus to (1) provide a dual or multiple output force for the spring shaftseal to vary the volume and, of prime importance, changing the effective cross-section area of the piston shaft of the spring cylinder near the end of the compression stroke, and (2) to provide a special extra volume chamber in the spring cylinder with asealed partition wall between the extra chamber and the operative volume part of the spring cylinder and having an auxiliary supply of gas under higher pressure than that of the spring operative gas pressures and with the spring shaft seal and thepartition wall seal made from specific material so that gas permeability characteristics of both seals are as desired to compensate for various conditions which cause leakage from the cylinder. As desired, the gas spring used in the counterbalanceapparatus can be used with or without any or all of the above noted enhancements to this spring operation.
In conjunction with the foregoing improvement in the dual or multiple force output provisions of the pneumatic spring unit, further objects reside in providing such a spring for substantially vertical disposition filled with a predeterminedquantity of oil or the like to enable operation as a liquid pneumatic shock absorber with plural output forces enabled by controlled movement of the shaft to cylinder sealing assembly near the retraction limit position of the shaft. Another object inconnection herewith resides in the incorporation of a supplemental disc valve unit which is located near the closed end of the spring cylinder and is provided with an orifice bleed to enable controlled movement, at least in the rebound direction ofmovement of the counterbalance unit when the shaft is retracted to the higher output force position. The disc valve can be fixed with a small axial floating movement to shift from an effective sealed relationship of its periphery with the cylinder wallto a free flow relationship so that orifice controlled flow is only in the direction of shaft extension under the high output force. The disc can be fixed in the cylinder wall to provide orifice controlled flow in both directions if so desired.
The invention may be embodied in other specific forms without departing from the spirit or essential characteristics thereof. The present embodiments are therefore to be considered in all respects as illustrative and not restrictive, the scopeof the invention being indicated by the appended claims rather than by the foregoing description, and all changes which come within the meaning and rage of equivalency of the claims are therefore intended to be embraced therein.
Counterbalance apparatus with transverse pneumatic spring and bellcrank linkage
Articles known as pneumatic or gas springs, which for convenience can be referred to as counterbalance links have become common in commercial articles, particularly in the automotive industry, but they are being used in many other fields whereverthe need is present to provide a counterbalance force for closure units, such as lids, doors and cabinet fronts, and gas spring replacement for mechanical spring fittings has become prevalent. In some fields of use, particularly in the automotive fieldwhere pneumatic springs are used on each side of trunk lids and hatch backs, the springs counterbalance the weight of the lid or hatch back. The gas springs are retracted, i.e., the spring piston rod is moved into the spring cylinder, when the lids areclosed. Then the gas spring units can extend, under gas pressure force acting on the effective piston shaft cross-section area, to move the lid to an open position. As is true of many gas springs, a control orifice by-pass in the gas spring,effectively slows the opening speed of the lid.
In the automotive field, particularly where pneumatic springs are used on hoods, trunk lids and hatch backs, two springs are used, primarily to provide balanced spaced apart forces to counterbalance the weight of the closure and prevent twistingor warping of the closure unit relative to its hinge axis. This invention while developed relative to automotive uses is not restricted to such field. It results in a compact installation using a single pneumatic spring connected through bell cranksand idler links to a hinged closure member. The elongate spring is mounted on and between bellcranks with the spring floating, between positions, in a direction transverse to the hinge axis of the closure. In conjunction with the counterbalanceapparatus the pneumatic spring construction has been improved to provide a desired multi-output force feature as well as incorporating a unique method and structure to effectively decrease loss of operative gas pressure within the pneumatic springresulting primarily from leakage of the gas directly through the shaft seal due to permeability of the material from which the seal is made. The latter aspect can be referred to as permeability compensation or pressure decay compensation.
Examples of transverse springs with bellcrank linkage are seen in the following U.S. Patents: U.S. Pat. No. 3,724,797 to H Freitaz et al for Resilient Seat; U.S. Pat. No. 4,416,094 to F. Bugener et al for Attic Window Assembly; and U.S. Pat. No. Re. 26,162 to A. K. Simons et al for Vehicle Seat Rebound Control. An example of a different dual output force concept in a pneumatic spring can be seen in applicant's U.S. Pat. No. 4,451,964 (also U.S. Pat. No. 4,451,978) where afloating piston is utilized to provide the dual output force. While not teaching the pressure decay compensation invention of this application, U.S. Pat. No. 4,408,751 to Daniel P. Dodson and George C. Ludwig for Multi-chamber Temperature CompensatedPneumatic Counterbalance shows a fixed partition or wall module providing a separate gas chamber in a pneumatic counterbalance cylinder.
A transversely mounted single pneumatic spring, bell crank and idler link assembly or apparatus will provide a compact installation for hinged closures such as automobile trunk lids or doors and other similar closures. The spring will float,being attached only to spaced-apart bellcranks. In an automobile trunk installation, where the trunk lid is mounted by hinges or "goosenecks" between each side of the lid and automobile frame, the forward space required for this counterbalance assemblyis minimized being installed laterally just behind the rear seat and in the forward upper portion of the trunk. Only one spring unit is required, thus minimizing cost. The spring unit is effectively hidden or concealed at the front upper part of thetrunk minimizing damage by items placed in the trunk. Other pneumatic spring enhancements, such as the multi-output force feature of the present invention and the pressure decay compensation feature of the present invention can be incorporated in thespring unit to provide convenient operation of opening the lid and to improve the life expectancy of the pneumatic spring by minimizing and effectively negating pressure loss due to leakage of gas past the shaft seal. If desired, other features such astemperature compensation as taught in U.S. Pat. No. 4,408,751 can be easily added to the pneumatic spring inasmuch as the spring cylinder length can be made substantially longer than the piston shaft, the stroke of which is relatively short. Excesscylinder length provides the space or volume zones used for the various, above mentioned, enhancement features.
The present invention has for a primary object the provision of a compact counterbalance apparatus for use with closure units where a single elongate pneumatic spring having shaft and cylinder end connector links are connected to arms of twospaced apart bellcranks, the other arms of which connect with idler links to a closure unit, secured for hinged movement to the frame structure of the closure, e.g., an autombile trunk lid with associated vehicle frame structure, the spring beingsupported laterally on the bellcranks so it floats in a plane parallel with the hinge axis of the closure lid.
Additional novel objects reside in the provision of improvements in the pneumatic springs which can be used with the aforementioned transverse spring and bell-crank apparatus to (1) provide a dual or multiple output force for the spring shaftseal to vary the volume and, of prime importance, changing the effective cross-section area of the piston shaft of the spring cylinder near the end of the compression stroke, and (2) to provide a special extra volume chamber in the spring cylinder with asealed partition wall between the extra chamber and the operative volume part of the spring cylinder and having an auxiliary supply of gas under higher pressure than that of the spring operative gas pressures and with the spring shaft seal and thepartition wall seal made from specific material so that gas permeability characteristics of both seals are as desired to compensate for various conditions which cause leakage from the cylinder. As desired, the gas spring used in the counterbalanceapparatus can be used with or without any or all of the above noted enhancements to this spring operation.
In conjunction with the foregoing improvement in the dual or multiple force output provisions of the pneumatic spring unit, further objects reside in providing such a spring for substantially vertical disposition filled with a predeterminedquantity of oil or the like to enable operation as a liquid pneumatic shock absorber with plural output forces enabled by controlled movement of the shaft to cylinder sealing assembly near the retraction limit position of the shaft. Another object inconnection herewith resides in the incorporation of a supplemental disc valve unit which is located near the closed end of the spring cylinder and is provided with an orifice bleed to enable controlled movement, at least in the rebound direction ofmovement of the counterbalance unit when the shaft is retracted to the higher output force position. The disc valve can be fixed with a small axial floating movement to shift from an effective sealed relationship of its periphery with the cylinder wallto a free flow relationship so that orifice controlled flow is only in the direction of shaft extension under the high output force. The disc can be fixed in the cylinder wall to provide orifice controlled flow in both directions if so desired.
Using the spring link construction previously described, a multiple load path for the multiple output capability of the spring link can be accomplished by providing independent mechanical linkage connecting or abutting the bushing abutment, apartfrom the shaft abutment parts which are used in FIGS. 8 and 17. It is further noted that the multiple part telescoped bushing embodiment offers numerous capabilities, e.g., a universal construction can be mass-produced for economic efficiency and thenduring specific uses, all bushing parts can be pushed in simultaneously, providing a dual stage spring; only the inner bushing part can be pushed in and provides a dual stage spring with a reduced output force of the second stage; or the shaft abutmentcan be eliminated completely to provide a conventional normal output spring. Thus, one can appreciate the universal capabilities of the multiple bushing part concept.
The invention may be embodied in other specific forms without departing from the spirit or essential characteristics thereof. The present embodiments are therefore to be considered in all respects as illustrative and not restrictive, the scopeof the invention being indicated by the appended claims rather than by the foregoing description, and all changes which come within the meaning and rage of equivalency of the claims are therefore intended to be embraced therein.
In the automotive field, particularly where pneumatic springs are used on hoods, trunk lids and hatch backs, two springs are used, primarily to provide balanced spaced apart forces to counterbalance the weight of the closure and prevent twistingor warping of the closure unit relative to its hinge axis. This invention while developed relative to automotive uses is not restricted to such field. It results in a compact installation using a single pneumatic spring connected through bell cranksand idler links to a hinged closure member. The elongate spring is mounted on and between bellcranks with the spring floating, between positions, in a direction transverse to the hinge axis of the closure. In conjunction with the counterbalanceapparatus the pneumatic spring construction has been improved to provide a desired multi-output force feature as well as incorporating a unique method and structure to effectively decrease loss of operative gas pressure within the pneumatic springresulting primarily from leakage of the gas directly through the shaft seal due to permeability of the material from which the seal is made. The latter aspect can be referred to as permeability compensation or pressure decay compensation.
Examples of transverse springs with bellcrank linkage are seen in the following U.S. Patents: U.S. Pat. No. 3,724,797 to H Freitaz et al for Resilient Seat; U.S. Pat. No. 4,416,094 to F. Bugener et al for Attic Window Assembly; and U.S. Pat. No. Re. 26,162 to A. K. Simons et al for Vehicle Seat Rebound Control. An example of a different dual output force concept in a pneumatic spring can be seen in applicant's U.S. Pat. No. 4,451,964 (also U.S. Pat. No. 4,451,978) where afloating piston is utilized to provide the dual output force. While not teaching the pressure decay compensation invention of this application, U.S. Pat. No. 4,408,751 to Daniel P. Dodson and George C. Ludwig for Multi-chamber Temperature CompensatedPneumatic Counterbalance shows a fixed partition or wall module providing a separate gas chamber in a pneumatic counterbalance cylinder.
A transversely mounted single pneumatic spring, bell crank and idler link assembly or apparatus will provide a compact installation for hinged closures such as automobile trunk lids or doors and other similar closures. The spring will float,being attached only to spaced-apart bellcranks. In an automobile trunk installation, where the trunk lid is mounted by hinges or "goosenecks" between each side of the lid and automobile frame, the forward space required for this counterbalance assemblyis minimized being installed laterally just behind the rear seat and in the forward upper portion of the trunk. Only one spring unit is required, thus minimizing cost. The spring unit is effectively hidden or concealed at the front upper part of thetrunk minimizing damage by items placed in the trunk. Other pneumatic spring enhancements, such as the multi-output force feature of the present invention and the pressure decay compensation feature of the present invention can be incorporated in thespring unit to provide convenient operation of opening the lid and to improve the life expectancy of the pneumatic spring by minimizing and effectively negating pressure loss due to leakage of gas past the shaft seal. If desired, other features such astemperature compensation as taught in U.S. Pat. No. 4,408,751 can be easily added to the pneumatic spring inasmuch as the spring cylinder length can be made substantially longer than the piston shaft, the stroke of which is relatively short. Excesscylinder length provides the space or volume zones used for the various, above mentioned, enhancement features.
The present invention has for a primary object the provision of a compact counterbalance apparatus for use with closure units where a single elongate pneumatic spring having shaft and cylinder end connector links are connected to arms of twospaced apart bellcranks, the other arms of which connect with idler links to a closure unit, secured for hinged movement to the frame structure of the closure, e.g., an autombile trunk lid with associated vehicle frame structure, the spring beingsupported laterally on the bellcranks so it floats in a plane parallel with the hinge axis of the closure lid.
Additional novel objects reside in the provision of improvements in the pneumatic springs which can be used with the aforementioned transverse spring and bell-crank apparatus to (1) provide a dual or multiple output force for the spring shaftseal to vary the volume and, of prime importance, changing the effective cross-section area of the piston shaft of the spring cylinder near the end of the compression stroke, and (2) to provide a special extra volume chamber in the spring cylinder with asealed partition wall between the extra chamber and the operative volume part of the spring cylinder and having an auxiliary supply of gas under higher pressure than that of the spring operative gas pressures and with the spring shaft seal and thepartition wall seal made from specific material so that gas permeability characteristics of both seals are as desired to compensate for various conditions which cause leakage from the cylinder. As desired, the gas spring used in the counterbalanceapparatus can be used with or without any or all of the above noted enhancements to this spring operation.
In conjunction with the foregoing improvement in the dual or multiple force output provisions of the pneumatic spring unit, further objects reside in providing such a spring for substantially vertical disposition filled with a predeterminedquantity of oil or the like to enable operation as a liquid pneumatic shock absorber with plural output forces enabled by controlled movement of the shaft to cylinder sealing assembly near the retraction limit position of the shaft. Another object inconnection herewith resides in the incorporation of a supplemental disc valve unit which is located near the closed end of the spring cylinder and is provided with an orifice bleed to enable controlled movement, at least in the rebound direction ofmovement of the counterbalance unit when the shaft is retracted to the higher output force position. The disc valve can be fixed with a small axial floating movement to shift from an effective sealed relationship of its periphery with the cylinder wallto a free flow relationship so that orifice controlled flow is only in the direction of shaft extension under the high output force. The disc can be fixed in the cylinder wall to provide orifice controlled flow in both directions if so desired.
Using the spring link construction previously described, a multiple load path for the multiple output capability of the spring link can be accomplished by providing independent mechanical linkage connecting or abutting the bushing abutment, apartfrom the shaft abutment parts which are used in FIGS. 8 and 17. It is further noted that the multiple part telescoped bushing embodiment offers numerous capabilities, e.g., a universal construction can be mass-produced for economic efficiency and thenduring specific uses, all bushing parts can be pushed in simultaneously, providing a dual stage spring; only the inner bushing part can be pushed in and provides a dual stage spring with a reduced output force of the second stage; or the shaft abutmentcan be eliminated completely to provide a conventional normal output spring. Thus, one can appreciate the universal capabilities of the multiple bushing part concept.
The invention may be embodied in other specific forms without departing from the spirit or essential characteristics thereof. The present embodiments are therefore to be considered in all respects as illustrative and not restrictive, the scopeof the invention being indicated by the appended claims rather than by the foregoing description, and all changes which come within the meaning and rage of equivalency of the claims are therefore intended to be embraced therein.
Pneumatic brake booster
In the design and manufacture of automobiles brake systems, decreasing the stopping distance of the vehicle when the brakes have been applied has frequently been a focus. Systems have been developed to generate maximum braking power within a fraction of a second, depending on the input rate from the driver.
Typically, panic devices located within the brake booster are used to accomplish this function. The brake booster amplifies the input force applied by the driver's foot on the brake pedal. A brake booster is comprised of front and rear chambers which are housed within a sealed volume. The front and rear chambers are separated by a flexible diaphragm membrane which prevents any type of pressure communication between the two chambers. In addition, brake boosters contain an input member of which the vehicle operator uses to engage the brake booster. When the braking system is at-rest, i.e., the driver's foot is off the brake pedal, both front and rear chambers are evacuated and in equilibrium. When the driver actuates the brake pedal, a mechanical valve is opened which allows air to flow into the rear chamber creating a pressure differential across the membrane.
This pressure differential acts over the membrane area and thus creates an output boost force which is generated on the piston reaction surface. The output force of the booster is the input force (from the brake pedal) plus the boost force. In this manner, the force of the driver's foot on the brake pedal is boosted to improve the force required of the driver for a deceleration.
Modern pneumatic brake boosters create a feedback force which acts in the opposite direction of the output force. The feedback force is transmitted through the brake pedal and gives the driver an indication of the current brake force. The feedback force is generated from the pressure and extrusion of the elastomer reaction disc acting in such a way as to close off the working diaphragm chambers from atmospheric pressure and allows the chambers to evacuate, thus reducing the output force. The feedback force is dependent upon the output force and increases as the output force increases. Such a system works sufficiently for average brake apply conditions. However, in an emergency condition where a short braking distance is critical, the feedback force may act to increase the braking distance by creating additional force required by the driver of the vehicle.
Several systems have been designed to reduce or eliminate the feedback force in emergency situations. For example, U.S. Pat. No. 6,186,042 issued Feb. 13, 2001 to Roland Levrai et al (hereafter "Levrai") discloses a "latching" type brake booster. The Levrai booster allows a braking force to be maintained even if the operator terminates the input force (removes his/her foot from the brake pedal) by locking the air valve position relative to the power piston if an emergency condition is detected. This, however, is undesirable since it removes control from the driver and gives no feedback with respect to status of the brake system.
In one aspect of the present invention, a pneumatic brake booster is provided. The pneumatic brake booster includes a generally cylindrical shaped piston having a first piston end and a second piston end. The piston defines a chamber at the first piston end and a piston bore at the second piston end separated by an air flow aperture. The piston bore has a plunger aperture located at the second piston end. The pneumatic brake booster also includes a plunger having a first plunger end and a second plunger end. The plunger is moveable between first and second positions and is located within the plunger aperture. An air valve has a first valve end and a second valve end and is moveable between first and second positions and defines a valve bore for receiving the first plunger end. A collapsing spring is located within the valve bore and is adapted to couple the plunger and the air valve. The plunger and the air valve are spaced apart a first relative distance in response to the pneumatic brake booster being in a regular apply mode and spaced apart a second relative distance in response to the pneumatic brake booster being in a panic apply mode.
In another aspect of the present invention, a pneumatic brake booster, is provided. The pneumatic brake booster includes a generally cylindrical shaped piston having a first piston end and a second piston end. The piston defines a chamber at the first piston end and a piston bore at the second piston end separated by an air flow aperture. The piston bore has a plunger aperture located at the second piston end. The pneumatic brake booster further includes a plunger, an air valve, and a sleeve. The plunger has a first plunger end and a second plunger end and is moveable between first and second positions. The second plunger end is located within the plunger aperture. The plunger includes a plunger trench which is located near the first end of the plunger. The air valve has a first valve end and a second valve end. The second valve end includes a bearing aperture and defines a valve bore for receiving the first plunger end. The sleeve includes a sleeve bore for receiving the second valve end and includes a sleeve trench located around an interior surface of the sleeve.
The pneumatic brake booster further includes at least one ball bearing located within the bearing aperture and being adapted to fit alternatively in the plunger trench or the sleeve trench.
Typically, panic devices located within the brake booster are used to accomplish this function. The brake booster amplifies the input force applied by the driver's foot on the brake pedal. A brake booster is comprised of front and rear chambers which are housed within a sealed volume. The front and rear chambers are separated by a flexible diaphragm membrane which prevents any type of pressure communication between the two chambers. In addition, brake boosters contain an input member of which the vehicle operator uses to engage the brake booster. When the braking system is at-rest, i.e., the driver's foot is off the brake pedal, both front and rear chambers are evacuated and in equilibrium. When the driver actuates the brake pedal, a mechanical valve is opened which allows air to flow into the rear chamber creating a pressure differential across the membrane.
This pressure differential acts over the membrane area and thus creates an output boost force which is generated on the piston reaction surface. The output force of the booster is the input force (from the brake pedal) plus the boost force. In this manner, the force of the driver's foot on the brake pedal is boosted to improve the force required of the driver for a deceleration.
Modern pneumatic brake boosters create a feedback force which acts in the opposite direction of the output force. The feedback force is transmitted through the brake pedal and gives the driver an indication of the current brake force. The feedback force is generated from the pressure and extrusion of the elastomer reaction disc acting in such a way as to close off the working diaphragm chambers from atmospheric pressure and allows the chambers to evacuate, thus reducing the output force. The feedback force is dependent upon the output force and increases as the output force increases. Such a system works sufficiently for average brake apply conditions. However, in an emergency condition where a short braking distance is critical, the feedback force may act to increase the braking distance by creating additional force required by the driver of the vehicle.
Several systems have been designed to reduce or eliminate the feedback force in emergency situations. For example, U.S. Pat. No. 6,186,042 issued Feb. 13, 2001 to Roland Levrai et al (hereafter "Levrai") discloses a "latching" type brake booster. The Levrai booster allows a braking force to be maintained even if the operator terminates the input force (removes his/her foot from the brake pedal) by locking the air valve position relative to the power piston if an emergency condition is detected. This, however, is undesirable since it removes control from the driver and gives no feedback with respect to status of the brake system.
In one aspect of the present invention, a pneumatic brake booster is provided. The pneumatic brake booster includes a generally cylindrical shaped piston having a first piston end and a second piston end. The piston defines a chamber at the first piston end and a piston bore at the second piston end separated by an air flow aperture. The piston bore has a plunger aperture located at the second piston end. The pneumatic brake booster also includes a plunger having a first plunger end and a second plunger end. The plunger is moveable between first and second positions and is located within the plunger aperture. An air valve has a first valve end and a second valve end and is moveable between first and second positions and defines a valve bore for receiving the first plunger end. A collapsing spring is located within the valve bore and is adapted to couple the plunger and the air valve. The plunger and the air valve are spaced apart a first relative distance in response to the pneumatic brake booster being in a regular apply mode and spaced apart a second relative distance in response to the pneumatic brake booster being in a panic apply mode.
In another aspect of the present invention, a pneumatic brake booster, is provided. The pneumatic brake booster includes a generally cylindrical shaped piston having a first piston end and a second piston end. The piston defines a chamber at the first piston end and a piston bore at the second piston end separated by an air flow aperture. The piston bore has a plunger aperture located at the second piston end. The pneumatic brake booster further includes a plunger, an air valve, and a sleeve. The plunger has a first plunger end and a second plunger end and is moveable between first and second positions. The second plunger end is located within the plunger aperture. The plunger includes a plunger trench which is located near the first end of the plunger. The air valve has a first valve end and a second valve end. The second valve end includes a bearing aperture and defines a valve bore for receiving the first plunger end. The sleeve includes a sleeve bore for receiving the second valve end and includes a sleeve trench located around an interior surface of the sleeve.
The pneumatic brake booster further includes at least one ball bearing located within the bearing aperture and being adapted to fit alternatively in the plunger trench or the sleeve trench.
Quick coupling device for a gas pressurization system
The present invention provides a novel regulator-valve combination which can be quickly coupled to form a rigid, leak proof, gas pressurization system. Although throughout the description provided herein, reference is made to a beveragedispensing system, it is to be understood that this invention can be utilized in any type of gas pressurization system which can be adapted for use with compressed gas storage cylinders. In addition, even though reference may be made to the use ofcarbon dioxide gas, the invention can be used with any gas desired. In a beverage dispensing system it is mandatory that a completely foolproof and safe arrangement be provided. This is especially true in a home dispenser system wherein the average person is required to operate and maintain the system whichincludes the changing of the pressurized gas storage cylinders. Thus, a simple and completely foolproof system is required to eliminate danger to the individual operating the system regardless of his knowledge or background. Since there is considerablepotential energy stored in a pressurized gas system, extreme care must be provided in the design of the components to provide the maximum safeguards for use of the regulator and valve assembly.
The carbon dioxide pressurization system which is described herein for use with a beverage dispenser provides the pressurization and motive force for transferring the fluid beverage syrups or concentrates from their containers and through thedispenser nozzle as desired, as well as carbonating the water mixed with the syrup. The pressurization gas which is stored in a pressure cylinder usually has a gauge pressure within a range of 800-3000 psi depending upon the gas used. The actualworking pressure within the syrup storage bottles and carbonator is much lower and usually within the range of 30-100 psi. This lower pressure in the operating system is desirable from a safety standpoint and for quality control of the beverageproduced. It must be remembered that if the beverage is to be used in the home environment, nontechnical individuals are required to operate the system and to maintain and replenish the syrup and pressurized gas cylinders. For this reason, the lowestpossible operating pressure is desirable in this type of system. The present regulating and shutoff valves provided in the present invention are ideal for this use but can be used in any other pressurization system where exact pressure control and rapidpressurized gas bottle replacement convenience is desired.
This invention is primarily directed to a pressure regulator and a quick-coupling apparatus provided for joining a regulator and cylinder valve for operation and mounting. Most beverage dispensing systems are mounted within a bar or under acounter wherein the bottles containing the syrup, carbonator and pressurized gas cylinder are stored and concealed from view. The regulator of the present invention is arranged to the rigidly or semi-rigidly mounted to the cabinet or bar at a sufficientelevation above the base to allow clearance for the intended pressurized gas storage cylinder. The regulator can be mounted on a mounting plate or bracket which in turn can be attached or mounted to the cabinet. The bracket can have quick releasefasteners which allow the regulator to be removed from the bracket, if desired. Usually, a flexible hose is connected from the outlet of a high pressure regulator to the inlet connection of a secondary, lower pressure regulator for pressurizing thesyrup containers.
In order to pressurize and maintain the pressure on the system, the compressed gas storage cylinder valve is slidably coupled to the regulator and the cylinder is held upright on the cabinet base. A pivotable retaining yoke having an adjustableretaining screw is positioned over the valve and the retaining screw is turned inwardly to contact the cylinder valve and push the regulator boss into the valve to automatically open a biased shutoff poppet contained within. A peripheral seal isprovided around the boss of the regulator to automatically seal the high pressure gas connection between the valve and regulator. With the apparatus provided in the present invention, a storage cylinder can be quickly attached to the system in a safeoperating manner. The pressurized gas is introduced automatically to the pressure regulator upon connection of the cylinder without the necessity of manually opening or closing any valve.
The valve provided on the high pressure gas storage cylinder includes a safety burst disc mounted in the body of the valve to prevent over-pressurization of the cylinder which can occur during the filling operation or if heat is accidentallyapplied to the cylinder which could greatly increase the pressure of the gas contained therein. In the present arrangement, a vented safety plug is threadly inserted into the body of the valve with the burst disc designed for separation at a pressurewhich is the same as the maximum safe operating pressure for the cylinder.
The cylinder valve contains a slidable poppet which is biased so that the poppet and its associated seal is held in a closed position against a valve seat. This design is provided so that the pressurized gas within the cylinder will assist inapplying a force against the poppet to hold the poppet in the closed position. The application of a counter force on the poppet will cause the poppet to move away from the seat, allowing the gas to exit through the outlet of the valve. This outlet isprovided in the form of a passageway which is designed to fit a boss on the associated pressure regulator.
The pressure regulator which is used in the present invention is a biased diaphragm-type regulator wherein the spring biasing force can be adjusted by means of a threaded cap. A center eyelet is provided through the diaphragm and is arranged sothat the diaphragm can slidably move with respect to the eyelet so that any excess pressure which might exist within the cavity of the regulator can be vented. A pivotally mounted valve having an outwardly extending arm is arranged within the regulatorcavity. The valve can pivot toward or away from a valve seat to variably control or stop the flow of gas through a passageway extending inwardly from the inlet boss. The arm of the lever is positioned within the eyelet so that movement of the diaphragmwill control the valve movement to control the gas flow and thus, downstream pressure. An outlet fitting is provided in a port in the regulator cavity for the attachment of a hose or tube for pressurization of the dispenser containers.
With the mounting arrangement provided for the storage cylinder in the present invention the pivotable retaining yoke is of major importance in that it permits the sideways attachment of the gas cylinder in a confined space. The arrangement alsoprovides a rigid and safe method for mounting the storage cylinder to minimize the danger to the operator.
As an additional feature of the present invention, a pressure fill adapter is provided for easy and quick refilling of the storage cylinders with compressed gas. The adapter includes a pivotable yoke which has a retaining screw and a valveconnecting boss provided at the opposite base end. A flexible fill hose is connected to the boss through a passageway provided in the base end. The fill boss and yoke is identical to that provided on the system pressure regulator and includes an O-ringand groove provided on the outer surface for sealing against the internal bore provided in the cylinder valve. In use, the boss of the adapter is positioned in the opening of the valve and the pivotable yoke is placed in retaining position. Thethreaded retaining screw is turned inwardly so that the tip is positioned against the valve causing the fill boss to be inserted causing the valve poppet to be opened to allow pressurized gas to flow into the storage cylinder.
The high pressure gas in the fill boss can open the poppet by itself without the fill boss mechanically contacting and opening the poppet. This occurs when the force from the gas pressure exceeds the spring biasing force and causes the poppet toback away from the seat and open. This arrangement may be desirable to allow the cylinder valve to automatically close even without removal of the fill adapter when gas flow stops during the fill process.
The internal openings within the cylinder valve of the present invention are intentionally oversized to permit increased flow of gas and liquid during fill and pressurization use. This allows for rapid transfer of the gas and filling of thecylinders. It is emphasized that the explanation provided herein and the apparatus which is described is not intended to be limited to use only with carbon dioxide gas but any suitable gas desired for the intended purpose. This invention can be used withany pressurized system in which it is desired to provide a quick-disconnect installation of gas storage cylinders to a gas pressure regulating device in a safe, nonhazardous manner.
The carbon dioxide pressurization system which is described herein for use with a beverage dispenser provides the pressurization and motive force for transferring the fluid beverage syrups or concentrates from their containers and through thedispenser nozzle as desired, as well as carbonating the water mixed with the syrup. The pressurization gas which is stored in a pressure cylinder usually has a gauge pressure within a range of 800-3000 psi depending upon the gas used. The actualworking pressure within the syrup storage bottles and carbonator is much lower and usually within the range of 30-100 psi. This lower pressure in the operating system is desirable from a safety standpoint and for quality control of the beverageproduced. It must be remembered that if the beverage is to be used in the home environment, nontechnical individuals are required to operate the system and to maintain and replenish the syrup and pressurized gas cylinders. For this reason, the lowestpossible operating pressure is desirable in this type of system. The present regulating and shutoff valves provided in the present invention are ideal for this use but can be used in any other pressurization system where exact pressure control and rapidpressurized gas bottle replacement convenience is desired.
This invention is primarily directed to a pressure regulator and a quick-coupling apparatus provided for joining a regulator and cylinder valve for operation and mounting. Most beverage dispensing systems are mounted within a bar or under acounter wherein the bottles containing the syrup, carbonator and pressurized gas cylinder are stored and concealed from view. The regulator of the present invention is arranged to the rigidly or semi-rigidly mounted to the cabinet or bar at a sufficientelevation above the base to allow clearance for the intended pressurized gas storage cylinder. The regulator can be mounted on a mounting plate or bracket which in turn can be attached or mounted to the cabinet. The bracket can have quick releasefasteners which allow the regulator to be removed from the bracket, if desired. Usually, a flexible hose is connected from the outlet of a high pressure regulator to the inlet connection of a secondary, lower pressure regulator for pressurizing thesyrup containers.
In order to pressurize and maintain the pressure on the system, the compressed gas storage cylinder valve is slidably coupled to the regulator and the cylinder is held upright on the cabinet base. A pivotable retaining yoke having an adjustableretaining screw is positioned over the valve and the retaining screw is turned inwardly to contact the cylinder valve and push the regulator boss into the valve to automatically open a biased shutoff poppet contained within. A peripheral seal isprovided around the boss of the regulator to automatically seal the high pressure gas connection between the valve and regulator. With the apparatus provided in the present invention, a storage cylinder can be quickly attached to the system in a safeoperating manner. The pressurized gas is introduced automatically to the pressure regulator upon connection of the cylinder without the necessity of manually opening or closing any valve.
The valve provided on the high pressure gas storage cylinder includes a safety burst disc mounted in the body of the valve to prevent over-pressurization of the cylinder which can occur during the filling operation or if heat is accidentallyapplied to the cylinder which could greatly increase the pressure of the gas contained therein. In the present arrangement, a vented safety plug is threadly inserted into the body of the valve with the burst disc designed for separation at a pressurewhich is the same as the maximum safe operating pressure for the cylinder.
The cylinder valve contains a slidable poppet which is biased so that the poppet and its associated seal is held in a closed position against a valve seat. This design is provided so that the pressurized gas within the cylinder will assist inapplying a force against the poppet to hold the poppet in the closed position. The application of a counter force on the poppet will cause the poppet to move away from the seat, allowing the gas to exit through the outlet of the valve. This outlet isprovided in the form of a passageway which is designed to fit a boss on the associated pressure regulator.
The pressure regulator which is used in the present invention is a biased diaphragm-type regulator wherein the spring biasing force can be adjusted by means of a threaded cap. A center eyelet is provided through the diaphragm and is arranged sothat the diaphragm can slidably move with respect to the eyelet so that any excess pressure which might exist within the cavity of the regulator can be vented. A pivotally mounted valve having an outwardly extending arm is arranged within the regulatorcavity. The valve can pivot toward or away from a valve seat to variably control or stop the flow of gas through a passageway extending inwardly from the inlet boss. The arm of the lever is positioned within the eyelet so that movement of the diaphragmwill control the valve movement to control the gas flow and thus, downstream pressure. An outlet fitting is provided in a port in the regulator cavity for the attachment of a hose or tube for pressurization of the dispenser containers.
With the mounting arrangement provided for the storage cylinder in the present invention the pivotable retaining yoke is of major importance in that it permits the sideways attachment of the gas cylinder in a confined space. The arrangement alsoprovides a rigid and safe method for mounting the storage cylinder to minimize the danger to the operator.
As an additional feature of the present invention, a pressure fill adapter is provided for easy and quick refilling of the storage cylinders with compressed gas. The adapter includes a pivotable yoke which has a retaining screw and a valveconnecting boss provided at the opposite base end. A flexible fill hose is connected to the boss through a passageway provided in the base end. The fill boss and yoke is identical to that provided on the system pressure regulator and includes an O-ringand groove provided on the outer surface for sealing against the internal bore provided in the cylinder valve. In use, the boss of the adapter is positioned in the opening of the valve and the pivotable yoke is placed in retaining position. Thethreaded retaining screw is turned inwardly so that the tip is positioned against the valve causing the fill boss to be inserted causing the valve poppet to be opened to allow pressurized gas to flow into the storage cylinder.
The high pressure gas in the fill boss can open the poppet by itself without the fill boss mechanically contacting and opening the poppet. This occurs when the force from the gas pressure exceeds the spring biasing force and causes the poppet toback away from the seat and open. This arrangement may be desirable to allow the cylinder valve to automatically close even without removal of the fill adapter when gas flow stops during the fill process.
The internal openings within the cylinder valve of the present invention are intentionally oversized to permit increased flow of gas and liquid during fill and pressurization use. This allows for rapid transfer of the gas and filling of thecylinders. It is emphasized that the explanation provided herein and the apparatus which is described is not intended to be limited to use only with carbon dioxide gas but any suitable gas desired for the intended purpose. This invention can be used withany pressurized system in which it is desired to provide a quick-disconnect installation of gas storage cylinders to a gas pressure regulating device in a safe, nonhazardous manner.
Device for fitting components
A device of this nature is known from U.S. Pat. No. 2,344,127. This device is used to handle blind rivets which are suspended one behind the other in a rail and in the rail are forced towards the end of the rail by spring stress. At the end of the rail, there is a mechanism which closes off the opening of the rail which is present in that area and allows only a single blind rivet to be delivered each time. This delivery is carried out by means of a lever which is arranged on a setting tool and is mounted on the setting tool in such a manner that it can pivot about an axis. To deliver a blind rivet which is suspended in front of the opening in the rail, the lever is pivoted towards this opening, during which movement the lever is able to pick up a single blind rivet and pivot it into a position in which the blind rivet is inserted in the setting tool. The rail is arranged on the side of the setting tool and thus forms a single unit with the setting tool. The mechanism which is required to deliver a blind rivet while simultaneously unlocking the rail is of complicated design and is arranged on the setting tool in such a manner that it can be accessed freely from outside, so that if the tool is not handled carefully the delivery mechanism can easily become damaged. Moreover, this device is a relatively complicated structure.
The invention is based on the object of providing a device for conveying and fitting components which are to be inserted in a workpiece, of the type mentioned at the outset, which device is robust and of compact design with few parts. According to the invention, this is achieved by the fact that the opening merges into a receiving part for a single component, which receiving part is connected to the rail via a hinge and is aligned with this rail, and the rail, together with the receiving part, is mounted in a longitudinally displaceable manner in a guide in which the receiving part, in order to receive a component, is, in the pushed-back position of the rail, held in a receiving position in which it is aligned with the rail, the receiving part being arranged in such a way that, when the rail is pushed forward, the receiving part, together with the component, projects out of the guide and, via the hinge, pivots through approximately 90° into an eject position, in which the component, in order to be fitted, can be ejected from the receiving part by a ram arranged next to the guide and can be fitted in a workpiece.
In the pushed-back position of the rail, the receiving part, which is held in a receiving position aligned with the rail, acts as a component of the rail, and from this position the receiving part merely has to be pivoted away when the rail is pushed forward in order to move, together with a component, into the eject position. The ability of the receiving part to move with respect to the rail is ensured by the hinge, via which the receiving part is connected to the rail, and therefore components of simple structure are involved. The structure of the device in this case forms a closed arrangement, from which, in the eject position, only the relatively short receiving part is pivoted away, with the result that the device as a whole is protected from damage.
In order to feed a component to the receiving part, it is expedient to provide a stop on the rail, which stop, after a component has been fitted, stops the components in the rail when the latter is pushed back and presses these components towards the opening in the rail, the receiving part being pivoted back out of the eject position into its receiving position, which is aligned with the rail, by a deflector part which is arranged at the opening, so that the action of the stop causes the front component which is being guided in the rail to slide into the receiving part, the deflector part guiding the pivoting of the receiving part into the eject position when the rail is pushed forward. The deflector part, which may, for example, be formed by a rounded section arranged at the end of the rail, is a component of simple design which merely has to control the movement of the receiving part out of the receiving position into the eject position and back when the rail is pushed forward and pushed back.
In order to provide protection in particular against the components falling out of the rail when handling the device, the components are expediently guided in lateral longitudinal grooves in the rail, into which grooves projections of the components fit.
In order to protect against the component which has been guided into the eject position of the receiving part falling out when handling the device, it is expedient if clamping means for holding the component in the eject position are provided on the receiving part. However, it is also possible for this holding function to be given by the component itself, by providing appropriate clamping means on the component.
It is expedient to arrange a locking device, which releasably secures the receiving part in the eject position, on the guide. If the device, with the receiving part in the eject position, is then moved in any way with respect to a workpiece, in particular is guided into and held in a vertical position, the locking device secures the receiving part in its eject position, so that it cannot pivot under the influence of the force of gravity. The locking device used may be a magnet which uses its relatively low force to hold the receiving part in the eject position but readily releases the receiving part when the rail is pulled back, so that the receiving part can be pivoted back and transferred into its receiving position.
Furthermore, it is expedient to provide a magnet, which pulls the receiving part towards the deflector part, in the region of the receiving part and of the deflector part. Such a magnet makes the movement of the receiving part independent of gravity, since, by means of the magnet, the receiving part, when it pivots away from the rail, is pulled into the pivoted-away eject position by the force of the magnet, an operation which, under certain circumstances, has to be carried out against the force of gravity, when the device is being used in a corresponding way. This configuration therefore makes the device independent of the force of gravity and means that it can therefore be moved towards a workpiece which is to be fitted in any desired position.
The invention is based on the object of providing a device for conveying and fitting components which are to be inserted in a workpiece, of the type mentioned at the outset, which device is robust and of compact design with few parts. According to the invention, this is achieved by the fact that the opening merges into a receiving part for a single component, which receiving part is connected to the rail via a hinge and is aligned with this rail, and the rail, together with the receiving part, is mounted in a longitudinally displaceable manner in a guide in which the receiving part, in order to receive a component, is, in the pushed-back position of the rail, held in a receiving position in which it is aligned with the rail, the receiving part being arranged in such a way that, when the rail is pushed forward, the receiving part, together with the component, projects out of the guide and, via the hinge, pivots through approximately 90° into an eject position, in which the component, in order to be fitted, can be ejected from the receiving part by a ram arranged next to the guide and can be fitted in a workpiece.
In the pushed-back position of the rail, the receiving part, which is held in a receiving position aligned with the rail, acts as a component of the rail, and from this position the receiving part merely has to be pivoted away when the rail is pushed forward in order to move, together with a component, into the eject position. The ability of the receiving part to move with respect to the rail is ensured by the hinge, via which the receiving part is connected to the rail, and therefore components of simple structure are involved. The structure of the device in this case forms a closed arrangement, from which, in the eject position, only the relatively short receiving part is pivoted away, with the result that the device as a whole is protected from damage.
In order to feed a component to the receiving part, it is expedient to provide a stop on the rail, which stop, after a component has been fitted, stops the components in the rail when the latter is pushed back and presses these components towards the opening in the rail, the receiving part being pivoted back out of the eject position into its receiving position, which is aligned with the rail, by a deflector part which is arranged at the opening, so that the action of the stop causes the front component which is being guided in the rail to slide into the receiving part, the deflector part guiding the pivoting of the receiving part into the eject position when the rail is pushed forward. The deflector part, which may, for example, be formed by a rounded section arranged at the end of the rail, is a component of simple design which merely has to control the movement of the receiving part out of the receiving position into the eject position and back when the rail is pushed forward and pushed back.
In order to provide protection in particular against the components falling out of the rail when handling the device, the components are expediently guided in lateral longitudinal grooves in the rail, into which grooves projections of the components fit.
In order to protect against the component which has been guided into the eject position of the receiving part falling out when handling the device, it is expedient if clamping means for holding the component in the eject position are provided on the receiving part. However, it is also possible for this holding function to be given by the component itself, by providing appropriate clamping means on the component.
It is expedient to arrange a locking device, which releasably secures the receiving part in the eject position, on the guide. If the device, with the receiving part in the eject position, is then moved in any way with respect to a workpiece, in particular is guided into and held in a vertical position, the locking device secures the receiving part in its eject position, so that it cannot pivot under the influence of the force of gravity. The locking device used may be a magnet which uses its relatively low force to hold the receiving part in the eject position but readily releases the receiving part when the rail is pulled back, so that the receiving part can be pivoted back and transferred into its receiving position.
Furthermore, it is expedient to provide a magnet, which pulls the receiving part towards the deflector part, in the region of the receiving part and of the deflector part. Such a magnet makes the movement of the receiving part independent of gravity, since, by means of the magnet, the receiving part, when it pivots away from the rail, is pulled into the pivoted-away eject position by the force of the magnet, an operation which, under certain circumstances, has to be carried out against the force of gravity, when the device is being used in a corresponding way. This configuration therefore makes the device independent of the force of gravity and means that it can therefore be moved towards a workpiece which is to be fitted in any desired position.
Pneumatic booster
Boosters of this type conventionally comprise a casing inside which there is a piston formed from a hub and from a skirt to define a front chamber permanently connected to a vacuum source and a back or rear chamber selectively connected to either the front chamber or to the atmosphere by a valve means. The valve means being actuated by a control rod capable of pressing, by means of the front face of a plunger on the back face of a reaction disk securely fastened to a thrust rod. A return spring for the control rod is being arranged between the piston and the plunger. The valve means comprising a shutter interacting with a first circular valve seat formed on the plunger and a second circular valve seat formed on the piston. The shutter is formed from a flexible membrane fixed in a leaktight manner by its outer peripheral edge to the piston.
An example of such booster is illustrated in the document EP-A-0,004,477boosters, exhibit several drawbacks such as the following: in order to prevent the control rod from having too long an idle travel, the valve means must be designed so that the "shutter lift" between the shutter and the first valve seat is as small as possible. It therefore follows that, on braking, the passage offered to the atmospheric air towards the back chamber is reduced, and likewise the passage offered to the air of the back chamber towards the front chamber during brake release is also reduced.
Another drawback due to these reduced and turbulent air passages resides in the fact that the air is greatly slowed down in its various movements between the atmosphere, the back chamber and as a the front chamber, and the boosters have long response times.
In addition, the operation of these boosters can be accompanied by air suction noises, which may become troublesome as the structure of the hub of the piston has a single radial passage towards the back chamber and a single axial passage towards the front chamber may induce a high degree of turbulence in the moving air.
Another major drawback of the known boosters resides in the fact that the annular shutter element has a general frustoconical shape with an external mounting bead, associated with the element support of the shutter, in the tubular hub of the piston assembly. The active part of the shutter element is connected to the mounting bead by a thin web which flaring out towards the outside for its connection with the mounting bead.
In such an arrangement, the intermediate web element of the shutter element is subjected, during the useful life of the booster, to numerous flexural and compressive stresses which can, after a period of time, induce weakening at this point, of the elastomer material making up the shutter element.
In addition, in operation, this intermediate web part of the shutter element is subjected to a pressure differential between the atmosphere prevailing permanently inside the tubular hub, around the input rod, and the vacuum permanently prevailing in the annular chamber surrounding this intermediate web part of the shutter element and permanently connected to the front chamber, or vacuum chamber of the booster. This pressure differential, aside from contributing to fatigue of the intermediate web part, induces an axial force on the active part of the shutter element, which axial force adds to the force of the valve spring. The valve plunger must overcome such axial forces during each brake release phase to free the active part of the shutter element from the first shutter seat formed in the hub and to re-establish communication between the back working chamber of the booster and the vacuum chamber. Because all such forces imposes an oversizing of the return spring for the input rod resulting especially in a high force to be supplied by the driver in order to implement the booster, this force being known in the art by the term "attack force".
Likewise, the plunger has a surface, corresponding to a surface area defined by the first circular valve seat which is subjected to the same pressure differential and an axial force associated with the return spring of the input rod must also overcome to further increasing the attack force.
The brake booster disclosed in document FR-A-2,537,524, broadly recited in the preamble of the main claim herein, attempts to provide a solution to these drawbacks. However such brake boosters still comprises a conventional valve means housed in the tubular central part formed at the back of the casing of the booster which interacting with a modified plunger and have a significant surface area subjected to the pressure differential and therefore requiring a significant attack force. In addition, according to this document, not only must the casing of the booster be of special design, but also the structure of the piston hub has a single radial passage towards the back chamber and a single axial passage towards the front chamber.
Communication of air through such passage induces a high degree of turbulence in the moving air, which can be detrimental to the response time of the booster by the slowing down of the air which they impose, and which generate operational noises.
The known boosters thus generally have non-negligible surface areas permanently subjected to a pressure differential which significantly increases attack forces and return forces. In addition, these forces can vary as a function of the difference in the pressures prevailing in the booster. As a result the same booster installed in various vehicles will have different features. Thus, during manufacture, as many booster settings as there will be vehicle models to be equipped are provided, which considerably emburdens the planning of manufacture, storage and dispatch of the boosters. In addition, such a booster will have substantially different features according to whether the vehicle that it equips is at sea level or at high altitude.
The object of the present invention is consequently to provide a booster whose operation is silent, whose response time is as slow as possible, where the valve means do not pose any durability problem and where the attack force is constant regardless of the conditions of use, and can be adjusted practically to any desired value through a simple, reliable and economic fashion using a booster casing of conventional design. The jump of such a booster is adjustable in a simple fashion without removing the booster.
With this object, the subject of the invention is a booster in which the air passages between the atmosphere and the back chamber on the one hand, the back chamber and the front chamber on the other hand, have the greatest possible cross section without presenting obstacles which can generate turbulence, and wherein the valve means and plunger have as reduced as possible a surface area, and even capable of being zero, subjected to the pressure differential.
According to the invention, the flexible membrane forming the shutter is connected in a leaktight manner by its internal peripheral edge to a rigid tubular part sliding in a leaktight manner in a rear tubular part of the piston.
In an advantageous manner, the external diameter of the rigid tubular part of the shutter is substantially equal to the diameter of the first circular valve seat formed on the plunger.
According to equally advantageous features, the plunger is formed with a front tubular part sliding in a leaktight manner in the piston, the external diameter of this tubular front part is substantially equal to the diameter of the first circular valve seat formed on the plunger and the external diameters of the tubular front part of the plunger and of the rigid tubular part of the shutter are substantially equal.
An example of such booster is illustrated in the document EP-A-0,004,477boosters, exhibit several drawbacks such as the following: in order to prevent the control rod from having too long an idle travel, the valve means must be designed so that the "shutter lift" between the shutter and the first valve seat is as small as possible. It therefore follows that, on braking, the passage offered to the atmospheric air towards the back chamber is reduced, and likewise the passage offered to the air of the back chamber towards the front chamber during brake release is also reduced.
Another drawback due to these reduced and turbulent air passages resides in the fact that the air is greatly slowed down in its various movements between the atmosphere, the back chamber and as a the front chamber, and the boosters have long response times.
In addition, the operation of these boosters can be accompanied by air suction noises, which may become troublesome as the structure of the hub of the piston has a single radial passage towards the back chamber and a single axial passage towards the front chamber may induce a high degree of turbulence in the moving air.
Another major drawback of the known boosters resides in the fact that the annular shutter element has a general frustoconical shape with an external mounting bead, associated with the element support of the shutter, in the tubular hub of the piston assembly. The active part of the shutter element is connected to the mounting bead by a thin web which flaring out towards the outside for its connection with the mounting bead.
In such an arrangement, the intermediate web element of the shutter element is subjected, during the useful life of the booster, to numerous flexural and compressive stresses which can, after a period of time, induce weakening at this point, of the elastomer material making up the shutter element.
In addition, in operation, this intermediate web part of the shutter element is subjected to a pressure differential between the atmosphere prevailing permanently inside the tubular hub, around the input rod, and the vacuum permanently prevailing in the annular chamber surrounding this intermediate web part of the shutter element and permanently connected to the front chamber, or vacuum chamber of the booster. This pressure differential, aside from contributing to fatigue of the intermediate web part, induces an axial force on the active part of the shutter element, which axial force adds to the force of the valve spring. The valve plunger must overcome such axial forces during each brake release phase to free the active part of the shutter element from the first shutter seat formed in the hub and to re-establish communication between the back working chamber of the booster and the vacuum chamber. Because all such forces imposes an oversizing of the return spring for the input rod resulting especially in a high force to be supplied by the driver in order to implement the booster, this force being known in the art by the term "attack force".
Likewise, the plunger has a surface, corresponding to a surface area defined by the first circular valve seat which is subjected to the same pressure differential and an axial force associated with the return spring of the input rod must also overcome to further increasing the attack force.
The brake booster disclosed in document FR-A-2,537,524, broadly recited in the preamble of the main claim herein, attempts to provide a solution to these drawbacks. However such brake boosters still comprises a conventional valve means housed in the tubular central part formed at the back of the casing of the booster which interacting with a modified plunger and have a significant surface area subjected to the pressure differential and therefore requiring a significant attack force. In addition, according to this document, not only must the casing of the booster be of special design, but also the structure of the piston hub has a single radial passage towards the back chamber and a single axial passage towards the front chamber.
Communication of air through such passage induces a high degree of turbulence in the moving air, which can be detrimental to the response time of the booster by the slowing down of the air which they impose, and which generate operational noises.
The known boosters thus generally have non-negligible surface areas permanently subjected to a pressure differential which significantly increases attack forces and return forces. In addition, these forces can vary as a function of the difference in the pressures prevailing in the booster. As a result the same booster installed in various vehicles will have different features. Thus, during manufacture, as many booster settings as there will be vehicle models to be equipped are provided, which considerably emburdens the planning of manufacture, storage and dispatch of the boosters. In addition, such a booster will have substantially different features according to whether the vehicle that it equips is at sea level or at high altitude.
The object of the present invention is consequently to provide a booster whose operation is silent, whose response time is as slow as possible, where the valve means do not pose any durability problem and where the attack force is constant regardless of the conditions of use, and can be adjusted practically to any desired value through a simple, reliable and economic fashion using a booster casing of conventional design. The jump of such a booster is adjustable in a simple fashion without removing the booster.
With this object, the subject of the invention is a booster in which the air passages between the atmosphere and the back chamber on the one hand, the back chamber and the front chamber on the other hand, have the greatest possible cross section without presenting obstacles which can generate turbulence, and wherein the valve means and plunger have as reduced as possible a surface area, and even capable of being zero, subjected to the pressure differential.
According to the invention, the flexible membrane forming the shutter is connected in a leaktight manner by its internal peripheral edge to a rigid tubular part sliding in a leaktight manner in a rear tubular part of the piston.
In an advantageous manner, the external diameter of the rigid tubular part of the shutter is substantially equal to the diameter of the first circular valve seat formed on the plunger.
According to equally advantageous features, the plunger is formed with a front tubular part sliding in a leaktight manner in the piston, the external diameter of this tubular front part is substantially equal to the diameter of the first circular valve seat formed on the plunger and the external diameters of the tubular front part of the plunger and of the rigid tubular part of the shutter are substantially equal.
Wheel rim for a pneumatic tire
It relates in particular to a wheel rim of the type disclosed in co-pending European Patent Application No. 88300557.1 which corresponds to U.S. Pat. No. 4,836,260, where a one piece wheel rim is provided having a pair of axially spaced apart tapered bead seats, tire retaining flange located axially outwards of each bead seat and characterised by one flange having a reduced height portion having a length of 0.25 to 0.5 times the bead circumference and the reduced height portion being such that the flange height, measured from the heel point, which is the point of intersection of the nominal diameter and the nominal wheel width, is in the range of 0.15 to 0.6 times the height of the remainder of the flange to allow tire fitting.
The wheel rim of this prior invention may in some circumstances cause chafing of the tire in the bead region adjacent to the cut-away portion of the flange, and it is one object of the present invention to provide a wheel rim of one piece construction which has all the advantages of the previous application but which in addition avoids chafing of the tire bead adjacent to the cut-away region.
According to one aspect of the present invention a one piece wheel rim for a pneumatic tire is provided having a pair of axially spaced apart tapered bead seats, a tire retaining flange located axially outwards of each bead seat, said flange being in its radially inner region at an angle of A degrees to the radial direction of the wheel and being characterised by having a reduced height portion having a length of 0.25 to 0.5 times the bead seat circumference and the reduced height being such that the flange height, measured from the heel point, which is the point of intersection of the nominal diameter and the nominal wheel width is in the range of 0.15 and 0.6 times the height of the remainder of the flange, wherein the portion of the flange which is radially outside the reduced height portion is at an angle B degrees where angle B is greater than angle A to the radial direction so that a tire bead fitted to the wheel rim seats against the flange only to the height of the reduced height portion around the full circumference of the tire.
Preferably the angle B of the radially outer portion of the wheel rim is substantially greater than angle A; for example angle B when measured from the radial direction is preferably in the range of 10 to 75 degrees and more preferably in the range of 60 to 70 degrees.
The overall height of the flange, measured in the radial direction, is preferably similar to the flange height used in a conventional rim.
The resultant assembly, in having the flange cut-away, still allows the wheel to have only a minimal fitting well which is of substantially smaller depth than a normal wheel rim well and thus the wheel rim allows for a greater brake volume than for a conventional wheel rim. As in the case of the previous invention the minimal fitting well may be circumferentially continuous or indeed in some preferred arrangements may be very short in the circumferential direction. The minimal well may comprise only a flat connecting base between the axially inner edges of the tapered bead seats so that in fact the wheel appears to have no well whatsoever.
The reduced height portion of the flange has limited effective thickness so that it projects in the axial direction of the wheel rim only a short distance from the tyre bead contacting flange face. This is to ensure that the necessary skew of the tire as it is fitted with part of the bead in the shallow well does not cause even the reduced height portion to abnormally tension the bead reinforcement on assembly of the tire to the wheel rim.
The reduced height portion, where it joins the portion sloping at angle B, may be smoothly radius from one portion to the other or may have a progressively rising region which has its surface at the angle B but which gradually rises in height until the full flange extension B is provided. Preferably one end of the cut-away portion projects suddenly to the full flange shape at the angle B and at the other end of the cut-away there is a progressive gradual slope in the portion of the flange at angle B.
The wheel rim of this prior invention may in some circumstances cause chafing of the tire in the bead region adjacent to the cut-away portion of the flange, and it is one object of the present invention to provide a wheel rim of one piece construction which has all the advantages of the previous application but which in addition avoids chafing of the tire bead adjacent to the cut-away region.
According to one aspect of the present invention a one piece wheel rim for a pneumatic tire is provided having a pair of axially spaced apart tapered bead seats, a tire retaining flange located axially outwards of each bead seat, said flange being in its radially inner region at an angle of A degrees to the radial direction of the wheel and being characterised by having a reduced height portion having a length of 0.25 to 0.5 times the bead seat circumference and the reduced height being such that the flange height, measured from the heel point, which is the point of intersection of the nominal diameter and the nominal wheel width is in the range of 0.15 and 0.6 times the height of the remainder of the flange, wherein the portion of the flange which is radially outside the reduced height portion is at an angle B degrees where angle B is greater than angle A to the radial direction so that a tire bead fitted to the wheel rim seats against the flange only to the height of the reduced height portion around the full circumference of the tire.
Preferably the angle B of the radially outer portion of the wheel rim is substantially greater than angle A; for example angle B when measured from the radial direction is preferably in the range of 10 to 75 degrees and more preferably in the range of 60 to 70 degrees.
The overall height of the flange, measured in the radial direction, is preferably similar to the flange height used in a conventional rim.
The resultant assembly, in having the flange cut-away, still allows the wheel to have only a minimal fitting well which is of substantially smaller depth than a normal wheel rim well and thus the wheel rim allows for a greater brake volume than for a conventional wheel rim. As in the case of the previous invention the minimal fitting well may be circumferentially continuous or indeed in some preferred arrangements may be very short in the circumferential direction. The minimal well may comprise only a flat connecting base between the axially inner edges of the tapered bead seats so that in fact the wheel appears to have no well whatsoever.
The reduced height portion of the flange has limited effective thickness so that it projects in the axial direction of the wheel rim only a short distance from the tyre bead contacting flange face. This is to ensure that the necessary skew of the tire as it is fitted with part of the bead in the shallow well does not cause even the reduced height portion to abnormally tension the bead reinforcement on assembly of the tire to the wheel rim.
The reduced height portion, where it joins the portion sloping at angle B, may be smoothly radius from one portion to the other or may have a progressively rising region which has its surface at the angle B but which gradually rises in height until the full flange extension B is provided. Preferably one end of the cut-away portion projects suddenly to the full flange shape at the angle B and at the other end of the cut-away there is a progressive gradual slope in the portion of the flange at angle B.
Product vending system with pneumatic product delivery
Much of the merchandising of food and beverages and the vending of a large number of other retail products occurs in circumstances that are ancillary to some other marketing activity by which other products and services are sold. That other activity is the primary attraction that brings the customer onto the business premises of the merchant or causes the customer to enter into a business relationship with the merchant. For example, hotel and travel accommodations, entertainment and sports events, recreational activities, and routine service activities such as tending to automobile fueling and service, personal grooming services and waiting for services or business appointments all may provide the primary reasons for people to enter onto certain business premises or to engage in a communication with a business enterprise. Such customers then purchase goods or services which result in charges or other forms of payment being made for such services or products.
On the occasions of the presence on such business premises, such people often have a demand for other products, such as food or beverage products, and become potential customers of the merchandising of such other products. The demands for such other products in such circumstances are not the result of any particular purchasing effort made by such customers to obtain such products, but are rather demands arising out of inherent needs ancillary to the occasions that attracted the people to the business premises.
Accordingly, the success of the merchandising of products to such potential customers is largely based on the merchant having in place a system to take advantage of the opportunity to serve the customers' needs. The ability to provide the needed products to the customer with maximum convenience while avoiding extra effort and time commitments by the customer may be the key to the success of any additional sales activity by the merchant. On such occasions, the success in vending such ancillary products may be based more on the convenience and ease of the transaction to the customer than on the price. However, the practicality of providing such systems by the merchant may also be based on the convenience to the merchant in servicing such system without employing additional personnel or space consuming facilities to display or deliver the products or to register payment for the additional goods provided.
In prior art merchandising systems, the vending of food and other ancillary products to persons attending some event or being on business premises for some primary reason other than the purchase of such ancillary products has required a generally labor intensive and space consuming enterprise that often requires substantially different skills and expertise than the main business being conducted on the site. Engaging in the vending of such products can add substantially to the overall business effort and cost of the business, which is often impractical and not worthwhile to the merchant. The activity of vending some unrelated products to a business's customers requires a commitment by the business, which, in many cases, deters the business from engaging in the vending opportunity.
Customers of many businesses have idle time during which they could purchase merchandise and would purchase merchandise but for the reason that there is no opportunity to do so. For example, when fueling an automobile at a self-service gasoline pump island of a gasoline service station, several minutes are spend waiting for the tank to fill. During this time, the purchase of a soft drink or other product could be made by the gasoline customer who cannot conveniently leave the pump location while the vehicle is being fueled to enter the service building or to approach a vending machine. Such a gasoline customer may be provided with a card reader at the pump, which accepts a charge card account as payment for the fuel without the need to enter the station. Such a customer may therefore forego the expenditure of the additional time required to leave the fueled vehicle at the pump to purchase food, a beverage, or another marginally necessary product. Other customers spend time waiting for professional services, for service to be performed on vehicles, for appointments in barbershops and beauty salons, in ticket and admission lines and at a variety of other business locations. During this idle time, the opportunities to vend products to these customers is lost due to the difficulty and cost of providing or adapting a merchandising system to the occasions.
Difficulty in merchandising products to customers is due in part to the need to protectively store products for sale, particularly where the product is a beverage or other food product. For example, the retail sale of beverages for immediate consumption is typically carried out in one of two ways: either by over-the-counter sale by a server or attendant at a store or other indoor location or by mechanized unattended sale from a drink dispensing machine, which may be at an indoor or an outdoor location. Beverages that are to be sold for immediate consumption are usually stored at a refrigerated temperature that is several degrees above the freezing point of water. The refrigeration is most commonly achieved by cooling a storage enclosure within the store building that is otherwise maintained at a typical room temperature. In addition, in geographic locations where temperatures drop below freezing, some heating of the building that surrounds the beverage storage enclosure maintains the building at the room temperature. With outdoor dispensing machines, such machines are usually not employed at times where below freezing temperatures are expected.
Systems have been provided for the marketing of beverages such as juices and soft drinks at locations more convenient to consumers. Such locations have included many that are frequented by vehicular or pedestrian traffic, such as gas stations and entertainment facilities. These locations have included concession counters and convenience stores that have been integrated with the gas station or entertainment facility.
Outdoor retail locations such as the vehicle service islands of gas stations are increasingly being provided with payment devices such as credit card readers that are operatively connected with the vehicle service devices, such as the gasoline dispensing pumps, for use by a customer purchasing gasoline, for example, to pay for the purchase without leaving the vicinity of the vehicle. At such locations, the customer is, nonetheless, required to enter the adjacent store facility to purchase snacks or beverages. The logistics of purchasing such additional products subjects the customer to an additional inconvenience, requiring some additional time and effort, which, in a certain percentage of cases, the consumer elects to forego, resulting in a loss to the retailer of a potential sale. Furthermore, the use of card readers at self-service gasoline pumps provides the capability for completely unattended gasoline sales, with the customer delivering the purchased gasoline from the self-service pump and making automatic payment without the intervention of a service attendant. Such a capability makes possible the sale of gasoline at night or at other times when no attendant is on duty, since there is no cash that must be handled and no requirement for the added security incident to a facility at which cash will be accepted and stored. At such unattended facilities, conventional systems for providing additional products such as beverages to the gasoline customer are not readily adaptable.
The vending of sandwiches and other solid food products for immediate consumption in the facilities discussed above present similar problems. Such products must usually be contained in their individual packaging, must be protected from environmental conditions such as excess heat or cold, and are preferably cooled or heated prior to or upon vending so as to require a freezer or a heating device such as a broiler or microwave oven that is preferable not to maintain at the vending area. With carry-out and drive-through fast food facilities, prepared heated or cooled foods are selected by customers from limited lists, packaged, paid for, and delivered into the hands of the customer in a manual labor intensive operation, presenting similar problems.
Accordingly, there is a need in the retailing industry, particularly for the sale of cool beverages, or temperature maintained, cooled or heated food items at locations such as gas stations, for delivering and dispensing such products to the consumer at a location of maximum convenience.
On the occasions of the presence on such business premises, such people often have a demand for other products, such as food or beverage products, and become potential customers of the merchandising of such other products. The demands for such other products in such circumstances are not the result of any particular purchasing effort made by such customers to obtain such products, but are rather demands arising out of inherent needs ancillary to the occasions that attracted the people to the business premises.
Accordingly, the success of the merchandising of products to such potential customers is largely based on the merchant having in place a system to take advantage of the opportunity to serve the customers' needs. The ability to provide the needed products to the customer with maximum convenience while avoiding extra effort and time commitments by the customer may be the key to the success of any additional sales activity by the merchant. On such occasions, the success in vending such ancillary products may be based more on the convenience and ease of the transaction to the customer than on the price. However, the practicality of providing such systems by the merchant may also be based on the convenience to the merchant in servicing such system without employing additional personnel or space consuming facilities to display or deliver the products or to register payment for the additional goods provided.
In prior art merchandising systems, the vending of food and other ancillary products to persons attending some event or being on business premises for some primary reason other than the purchase of such ancillary products has required a generally labor intensive and space consuming enterprise that often requires substantially different skills and expertise than the main business being conducted on the site. Engaging in the vending of such products can add substantially to the overall business effort and cost of the business, which is often impractical and not worthwhile to the merchant. The activity of vending some unrelated products to a business's customers requires a commitment by the business, which, in many cases, deters the business from engaging in the vending opportunity.
Customers of many businesses have idle time during which they could purchase merchandise and would purchase merchandise but for the reason that there is no opportunity to do so. For example, when fueling an automobile at a self-service gasoline pump island of a gasoline service station, several minutes are spend waiting for the tank to fill. During this time, the purchase of a soft drink or other product could be made by the gasoline customer who cannot conveniently leave the pump location while the vehicle is being fueled to enter the service building or to approach a vending machine. Such a gasoline customer may be provided with a card reader at the pump, which accepts a charge card account as payment for the fuel without the need to enter the station. Such a customer may therefore forego the expenditure of the additional time required to leave the fueled vehicle at the pump to purchase food, a beverage, or another marginally necessary product. Other customers spend time waiting for professional services, for service to be performed on vehicles, for appointments in barbershops and beauty salons, in ticket and admission lines and at a variety of other business locations. During this idle time, the opportunities to vend products to these customers is lost due to the difficulty and cost of providing or adapting a merchandising system to the occasions.
Difficulty in merchandising products to customers is due in part to the need to protectively store products for sale, particularly where the product is a beverage or other food product. For example, the retail sale of beverages for immediate consumption is typically carried out in one of two ways: either by over-the-counter sale by a server or attendant at a store or other indoor location or by mechanized unattended sale from a drink dispensing machine, which may be at an indoor or an outdoor location. Beverages that are to be sold for immediate consumption are usually stored at a refrigerated temperature that is several degrees above the freezing point of water. The refrigeration is most commonly achieved by cooling a storage enclosure within the store building that is otherwise maintained at a typical room temperature. In addition, in geographic locations where temperatures drop below freezing, some heating of the building that surrounds the beverage storage enclosure maintains the building at the room temperature. With outdoor dispensing machines, such machines are usually not employed at times where below freezing temperatures are expected.
Systems have been provided for the marketing of beverages such as juices and soft drinks at locations more convenient to consumers. Such locations have included many that are frequented by vehicular or pedestrian traffic, such as gas stations and entertainment facilities. These locations have included concession counters and convenience stores that have been integrated with the gas station or entertainment facility.
Outdoor retail locations such as the vehicle service islands of gas stations are increasingly being provided with payment devices such as credit card readers that are operatively connected with the vehicle service devices, such as the gasoline dispensing pumps, for use by a customer purchasing gasoline, for example, to pay for the purchase without leaving the vicinity of the vehicle. At such locations, the customer is, nonetheless, required to enter the adjacent store facility to purchase snacks or beverages. The logistics of purchasing such additional products subjects the customer to an additional inconvenience, requiring some additional time and effort, which, in a certain percentage of cases, the consumer elects to forego, resulting in a loss to the retailer of a potential sale. Furthermore, the use of card readers at self-service gasoline pumps provides the capability for completely unattended gasoline sales, with the customer delivering the purchased gasoline from the self-service pump and making automatic payment without the intervention of a service attendant. Such a capability makes possible the sale of gasoline at night or at other times when no attendant is on duty, since there is no cash that must be handled and no requirement for the added security incident to a facility at which cash will be accepted and stored. At such unattended facilities, conventional systems for providing additional products such as beverages to the gasoline customer are not readily adaptable.
The vending of sandwiches and other solid food products for immediate consumption in the facilities discussed above present similar problems. Such products must usually be contained in their individual packaging, must be protected from environmental conditions such as excess heat or cold, and are preferably cooled or heated prior to or upon vending so as to require a freezer or a heating device such as a broiler or microwave oven that is preferable not to maintain at the vending area. With carry-out and drive-through fast food facilities, prepared heated or cooled foods are selected by customers from limited lists, packaged, paid for, and delivered into the hands of the customer in a manual labor intensive operation, presenting similar problems.
Accordingly, there is a need in the retailing industry, particularly for the sale of cool beverages, or temperature maintained, cooled or heated food items at locations such as gas stations, for delivering and dispensing such products to the consumer at a location of maximum convenience.
Portable pneumatic machine having embodied control electronics
The present invention relates to portable pneumatic machines of the type having a body with a compressed air inlet pipe or tube, rotary pneumatic drive means (bladed turbine or motor for exemple) placed in the body, actuated by the compressed airflow for rotating a tool, a device for adjusting or stopping the airflow feeding the machine and an electric generator including a rotor and a stator installed in the body. The rotor is arranged for being mechanically rotated by the drive means forcreating electric energy from the pneumatic power driving the tool.
The invention is particularly suitable, though not exclusively, for portable pneumatic screw drivers, drills, screwers and grinders.
Pneumatic machines of the above defined type are already known. The document FR-A-No. 2 523 891, relating to a rotary pneumatic machine which includes lighting, shows a machine with a rotary member driven by a mechanism enclosed in a case, andactuated by compressed air. The case, having for this purpose means for connection to a compressed air source, includes an electric generator with rotor and stator, the rotor of which is driven by the compressed air feeding mechanism of the machine. This rotor is enclosed in a housing fixable to the case. The generator energizes lightening means carried by the housing for allowing the machine to work in difficult accessible places where the use of a portable lamp is impossible. This machinenevertheless only has a limited interest.
It is another object of the invention to provide a machine including an electric generator having signal delivering means which comprise third signal means delivering a signal representative of the rotational speed of the rotary drive means. Theelectronic circuit for controlling and monitoring the machine has third selecting means for selecting a reference value of this speed and means for maintaining said speed at this reference value. An application of this particularly interestingembodiment may be made to grinders, sanders and other machines whose speed of rotation depends on the pressure exerted by the operator on the support to be machined.
Another object of the invention is to provide a pneumatic machine wherein the signal delivering means of the electric generator means include second signal means for transmitting to the electronic circuit a signal representative of the angularposition of the rotary drive means and of the tool, said electronic circuit having second selecting means for selecting a reference value of the angular position of the tool and for controlling the actuating device when the angular position of the toolreaches said reference value. With this arrangement, a screw may be screwed into a support of variable elasticity. An approximative approach brings the support and the screw into contact, this latter than being rotated through a predetermined angle.
Another object of the invention is to provide a portable pneumatic machine wherein the signal delivering means include first signal means for transmitting to the electronic circuit a signal representative of the torque exerted by the rotary drivemeans on the tool, said electronic circuit having first selecting means for selecting a torque reference value for the maximum output torque value of said rotary drive means and for controlling the actuating device when the torque value has reached saidreference value. When the torque has reached the reference value, the air is cut off.
An object of the invention is also to provide a portable screw driver wherein the electronic circuit further comprises measuring means for measuring the torque value increase during operation of the machine with respect to time, firstanticipating means for anticipating from said measuring of the torque value increase a remaining torque value increase necessary to follow for reaching the torque reference value, computing means setting a reference time to and deducing from saidremaining torque value increase a remaining tightening time t from said reference time to for reaching said torque reference value, and means for actuating the actuating device arranged to shut off the compressed air inlet pipe after the time tstarting from said reference time to, whereby the tool is precisely stopped when the torque reference value is reached.
The electronic circuit further comprises measuring means for measuring the torque value increase during operation of the machine with respect to angular position of the rotating drive means, second anticipating means for anticipating from saidmeasuring of the torque value increase a remaining torque value increase necessary to follow for reaching the torque reference value, computing means setting a reference angle αo and deducing from said remaining torque value increase aremaining tightening angle α from said reference angle αo to be rotated for reaching said torque reference value and means for actuating the actuating device arranged to shut off the compressed air inlet pipe after rotation of the angleα starting from said reference angle αo.
Such an arrangement allows to stop the tool at a very precise position. Effectively, if the shut off of the compressed air inlet pipe is actuated only when the reference or setting value is reached, a slight delay may occur before a completestop is attained, therefore inducing a slight overrun of said reference value.
With the above-mentioned means for measuring, anticipating, computing and controlling (with a temporisation for example) the actuating device, the shutting of the compressed air can be initiated slightly before reaching the reference value, inorder to obtain the stop of the tool very precisely at this reference value.
The portable pneumatic machine may also include elastic means wherein it further includes an elastic device arranged to slow the rotary drive means on operation therefore increasing time for reaching from a predetermined initial torque value, thetorque reference value, whereby it ameliorates tightening precision.
The invention is particularly suitable, though not exclusively, for portable pneumatic screw drivers, drills, screwers and grinders.
Pneumatic machines of the above defined type are already known. The document FR-A-No. 2 523 891, relating to a rotary pneumatic machine which includes lighting, shows a machine with a rotary member driven by a mechanism enclosed in a case, andactuated by compressed air. The case, having for this purpose means for connection to a compressed air source, includes an electric generator with rotor and stator, the rotor of which is driven by the compressed air feeding mechanism of the machine. This rotor is enclosed in a housing fixable to the case. The generator energizes lightening means carried by the housing for allowing the machine to work in difficult accessible places where the use of a portable lamp is impossible. This machinenevertheless only has a limited interest.
It is another object of the invention to provide a machine including an electric generator having signal delivering means which comprise third signal means delivering a signal representative of the rotational speed of the rotary drive means. Theelectronic circuit for controlling and monitoring the machine has third selecting means for selecting a reference value of this speed and means for maintaining said speed at this reference value. An application of this particularly interestingembodiment may be made to grinders, sanders and other machines whose speed of rotation depends on the pressure exerted by the operator on the support to be machined.
Another object of the invention is to provide a pneumatic machine wherein the signal delivering means of the electric generator means include second signal means for transmitting to the electronic circuit a signal representative of the angularposition of the rotary drive means and of the tool, said electronic circuit having second selecting means for selecting a reference value of the angular position of the tool and for controlling the actuating device when the angular position of the toolreaches said reference value. With this arrangement, a screw may be screwed into a support of variable elasticity. An approximative approach brings the support and the screw into contact, this latter than being rotated through a predetermined angle.
Another object of the invention is to provide a portable pneumatic machine wherein the signal delivering means include first signal means for transmitting to the electronic circuit a signal representative of the torque exerted by the rotary drivemeans on the tool, said electronic circuit having first selecting means for selecting a torque reference value for the maximum output torque value of said rotary drive means and for controlling the actuating device when the torque value has reached saidreference value. When the torque has reached the reference value, the air is cut off.
An object of the invention is also to provide a portable screw driver wherein the electronic circuit further comprises measuring means for measuring the torque value increase during operation of the machine with respect to time, firstanticipating means for anticipating from said measuring of the torque value increase a remaining torque value increase necessary to follow for reaching the torque reference value, computing means setting a reference time to and deducing from saidremaining torque value increase a remaining tightening time t from said reference time to for reaching said torque reference value, and means for actuating the actuating device arranged to shut off the compressed air inlet pipe after the time tstarting from said reference time to, whereby the tool is precisely stopped when the torque reference value is reached.
The electronic circuit further comprises measuring means for measuring the torque value increase during operation of the machine with respect to angular position of the rotating drive means, second anticipating means for anticipating from saidmeasuring of the torque value increase a remaining torque value increase necessary to follow for reaching the torque reference value, computing means setting a reference angle αo and deducing from said remaining torque value increase aremaining tightening angle α from said reference angle αo to be rotated for reaching said torque reference value and means for actuating the actuating device arranged to shut off the compressed air inlet pipe after rotation of the angleα starting from said reference angle αo.
Such an arrangement allows to stop the tool at a very precise position. Effectively, if the shut off of the compressed air inlet pipe is actuated only when the reference or setting value is reached, a slight delay may occur before a completestop is attained, therefore inducing a slight overrun of said reference value.
With the above-mentioned means for measuring, anticipating, computing and controlling (with a temporisation for example) the actuating device, the shutting of the compressed air can be initiated slightly before reaching the reference value, inorder to obtain the stop of the tool very precisely at this reference value.
The portable pneumatic machine may also include elastic means wherein it further includes an elastic device arranged to slow the rotary drive means on operation therefore increasing time for reaching from a predetermined initial torque value, thetorque reference value, whereby it ameliorates tightening precision.
Self-sealing vacuum hose swivel fitting
Swivel fittings between vacuum cleaner hoses and wands or tank end adapters of vacuum cleaners are well-represented by a plurality of designs in the art. Examples of such attachments include those disclosed in U.S. Pat. Nos. 2,427,456,2,621,048, and 3,928,715, as perhaps being most related to the disclosure of the present invention. The last identified patent discloses a pair of hose connectors fixed to the opposite ends of a vacuum hose and made integral therewith so that electricalconductors in the hose may be conveniently terminated in the hose connectors. The swivel connection is effected between the hose connector and the end of a wand or canister or tank. A separate spring and corrugated seal is shown in U.S. Pat. No.2,621,048, while a corrugated element in U.S. Pat. No. 2,427,456 acts both as a seal and the spring element. While presumably effective to satisfy the needs for which they were designed, the fittings disclosed in these patents do not meet thosecriteria which are felt to meet the need for a more effective hose fitting.
Specifically, it is desired that the fitting, which will attach a vacuum hose to a wand or tank end adapter, will allow the adapter to swivel freely and seal against air or fluid loss and to increase the seal upon increase in vacuum. It isfurther desired that the fitting design reduce the need for critical dimensional stability while, at the same time, reduce mold and inspection costs.
The present invention overcomes the disadvantages of the prior art and meets the above criteria by utilizing the natural spring characteristics inherent in the undulated wall of a hose to apply sealing pressure to the hose end and against asealing surface on the fitting. In this design, the hose is swivelable with respect to the fitting. Such a design further enables a simple electrical interconnection between the hose and the fitting.
Although the invention has been described with reference to particular embodiments thereof, it should be realized that various changes and modifications may be made therein without departing from the spirit and scope of the invention.
Specifically, it is desired that the fitting, which will attach a vacuum hose to a wand or tank end adapter, will allow the adapter to swivel freely and seal against air or fluid loss and to increase the seal upon increase in vacuum. It isfurther desired that the fitting design reduce the need for critical dimensional stability while, at the same time, reduce mold and inspection costs.
The present invention overcomes the disadvantages of the prior art and meets the above criteria by utilizing the natural spring characteristics inherent in the undulated wall of a hose to apply sealing pressure to the hose end and against asealing surface on the fitting. In this design, the hose is swivelable with respect to the fitting. Such a design further enables a simple electrical interconnection between the hose and the fitting.
Although the invention has been described with reference to particular embodiments thereof, it should be realized that various changes and modifications may be made therein without departing from the spirit and scope of the invention.
Wood Pneumatic Stools
Stools are among the most important and popular forms of seating in the work environment and at home. They are widely available from many seat manufacturers and comes in various shapes and sizes. A properly designed and fully adjustable stool, along with appropriate seating posture, play an important role in reducing back stress, fatigue and restricted blood circulation. It also assists in avoiding distractions caused by discomfort, which is triggered by inappropriate support and constantly requires adjustments to remain comfortable. Therefore, ergonomically designed wood pneumatic stools go hand in hand with healthy seating.
The selection of seating equipment is usually done with the assumption that one size fits all. However, this notion is untrue and should be avoided at all costs. Users have different body types and adjustments such as height should be considered to facilitate proper seating posture. Height adjusting mechanism ensures that the user is able to firmly place his/her feet on the ground, an important aspect of ergonomic positioning. Some work surfaces (e.g. drafting tables) require taller seating equipment and thus necessitate the presence of a foot ring to enable users to firmly place their feet and at the same time be able to reach the work surface comfortably. Wood pneumatic stools offer versatility and suffice different user requirements. A study revealed that pneumatic stools are more useful and are more adapted for workers who require constant height adjustment, than ordinary stools.
While choosing a wood pneumatic stool, it is essential to ensure that the casters are in accordance with the floor upon which they are intended to be used, a feature most people tend to forget. Soft floors like carpet, linoleum, rugs, etc. mandate 'soft floor casters' while hard floors like wood, tile, ceramic, etc. require 'hard floor casters'. A stool with a five star fiberglass reinforced nylon base should be selected for added stability. Also, the height adjustment mechanism should be easy to use and offer 360 degree height adjustment. It is also imperative that the height adjustment range be in sync with the user(s) requirement.
Apart from all the benefits it already has to offer, wood pneumatic stools blend well with decor and can be virtually used anywhere in the modern office or home. Therefore, wood pneumatic stools not only fulfill ergonomic seating needs, it also satisfies aesthetic requirements.
The selection of seating equipment is usually done with the assumption that one size fits all. However, this notion is untrue and should be avoided at all costs. Users have different body types and adjustments such as height should be considered to facilitate proper seating posture. Height adjusting mechanism ensures that the user is able to firmly place his/her feet on the ground, an important aspect of ergonomic positioning. Some work surfaces (e.g. drafting tables) require taller seating equipment and thus necessitate the presence of a foot ring to enable users to firmly place their feet and at the same time be able to reach the work surface comfortably. Wood pneumatic stools offer versatility and suffice different user requirements. A study revealed that pneumatic stools are more useful and are more adapted for workers who require constant height adjustment, than ordinary stools.
While choosing a wood pneumatic stool, it is essential to ensure that the casters are in accordance with the floor upon which they are intended to be used, a feature most people tend to forget. Soft floors like carpet, linoleum, rugs, etc. mandate 'soft floor casters' while hard floors like wood, tile, ceramic, etc. require 'hard floor casters'. A stool with a five star fiberglass reinforced nylon base should be selected for added stability. Also, the height adjustment mechanism should be easy to use and offer 360 degree height adjustment. It is also imperative that the height adjustment range be in sync with the user(s) requirement.
Apart from all the benefits it already has to offer, wood pneumatic stools blend well with decor and can be virtually used anywhere in the modern office or home. Therefore, wood pneumatic stools not only fulfill ergonomic seating needs, it also satisfies aesthetic requirements.
Pneumatic Conveying Systems
A pneumatic conveyor is a machine used to move materials throughout an industrial plant or manufacturing facility. Pneumatic conveyor systems serve as an alternate to mechanical conveyors such as belts and vibrating trays. Instead of using traditional motors, they rely on air pressure to draw materials from various containers and transport them to other parts of the building for mixing or processing. Each conveyor utilizes either forced-air pressure or vacuum technology to push or pull materials using air. Forced-air systems are best for moving materials to multiple locations using a split tubing or pipe configuration, while vacuum units can only pull materials to a single location.
These systems are used in many industries. In agricultural settings, a pneumatic grain conveyor moves corn and other grains into or out of silos and other storage tanks. Pneumatic conveyors are also widely used in chemical and pharmaceutical manufacturing, as well as in the thermoplastics industry. These systems help transport various ingredients for food processing, and may also be used to manufacture cosmetics and detergents. Some energy producers rely on a pneumatic conveyor system to move oil and other fuel products.
There are two basic types of pneumatic conveyor system to choose from, and each is characterized by how it transports materials. Dilute-phase systems move materials at very high speeds and pressure levels, which dilutes the products so they are suspended in the air within the system. Dense-phase conveyors move materials more slowly, so they are not suspended in the air. A dense-phase system may move liquids along a pipe, while a dilute-phase model might be used to blow minute grain particles through a duct or tube.
A pneumatic conveyor offers a number of advantages over comparable mechanical systems. They can be modified to fit almost any floor layout, and can be used to transport materials from different areas or levels of the building. They also run over a larger area, and are easier to maintain than mechanical conveyors. Finally, pneumatic systems tend to produce less dust and fewer emissions than belt-based conveyor systems.
Despite their many benefits, pneumatic conveyors are also associated with a number of potential drawbacks that may deter some buyers. They cost more in terms of upfront equipment costs, and often cost more to operate each month. The design is also more complex, and may require the assistance of professional designers or consultants in order to create an effective conveyor system.
These systems are used in many industries. In agricultural settings, a pneumatic grain conveyor moves corn and other grains into or out of silos and other storage tanks. Pneumatic conveyors are also widely used in chemical and pharmaceutical manufacturing, as well as in the thermoplastics industry. These systems help transport various ingredients for food processing, and may also be used to manufacture cosmetics and detergents. Some energy producers rely on a pneumatic conveyor system to move oil and other fuel products.
There are two basic types of pneumatic conveyor system to choose from, and each is characterized by how it transports materials. Dilute-phase systems move materials at very high speeds and pressure levels, which dilutes the products so they are suspended in the air within the system. Dense-phase conveyors move materials more slowly, so they are not suspended in the air. A dense-phase system may move liquids along a pipe, while a dilute-phase model might be used to blow minute grain particles through a duct or tube.
A pneumatic conveyor offers a number of advantages over comparable mechanical systems. They can be modified to fit almost any floor layout, and can be used to transport materials from different areas or levels of the building. They also run over a larger area, and are easier to maintain than mechanical conveyors. Finally, pneumatic systems tend to produce less dust and fewer emissions than belt-based conveyor systems.
Despite their many benefits, pneumatic conveyors are also associated with a number of potential drawbacks that may deter some buyers. They cost more in terms of upfront equipment costs, and often cost more to operate each month. The design is also more complex, and may require the assistance of professional designers or consultants in order to create an effective conveyor system.
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