WO1998021487A1 - An apparatus for reducing the consumption of compressed air in pneumatic machines - Google Patents
An apparatus for reducing the consumption of compressed air in pneumatic machines Download PDFInfo
- Publication number
- WO1998021487A1 WO1998021487A1 PCT/SE1996/001467 SE9601467W WO9821487A1 WO 1998021487 A1 WO1998021487 A1 WO 1998021487A1 SE 9601467 W SE9601467 W SE 9601467W WO 9821487 A1 WO9821487 A1 WO 9821487A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- valve
- return
- chamber
- working chamber
- piston
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/20—Other details, e.g. assembly with regulating devices
- F15B15/28—Means for indicating the position, e.g. end of stroke
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
- F15B11/046—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed depending on the position of the working member
- F15B11/048—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed depending on the position of the working member with deceleration control
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/20—Other details, e.g. assembly with regulating devices
- F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
- F15B15/223—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke having a piston with a piston extension or piston recess which completely seals the main fluid outlet as the piston approaches its end position
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
- F15B2211/7051—Linear output members
- F15B2211/7052—Single-acting output members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
- F15B2211/7051—Linear output members
- F15B2211/7053—Double-acting output members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/755—Control of acceleration or deceleration of the output member
Definitions
- the present invention relates to an apparatus for effectively utilizing compressed air in reciprocatable pneumatic machines, in particular pneumatic machines of the type which provide a strong primary working movement and a relatively weak return movement, or one or more secondary, stepwise weaker and weaker movements, and which machines therefore need a stronger compressed air force in one direction of movement than in the opposite direction.
- the invention is useful both for axially operating pneumatic machines, generally referred to as piston-cylinder units, and for rotary machines of reciprocatable type.
- the object of the invention is to solve the problem of eliminating the above mentioned lacks and disadvantages in pneumatic, reciprocatable machines providing a strong working stroke and a less strong return stroke and this is provided by a machine providing a strong primary movement by a pressure in a working chamber and a less strong return movement by a pressure in a return chamber, or by one or more secondary, stepwise softer movements, and in which the primary movement demands a stronger compressed air force than the return movement, and which pneumatic machine comprises a piston operating in a cylinder and which defines a working chamber and a return chamber, a valve formed with three or more functional positions for providing the different functional steps, and in which the valve, in a first position, provides a full pressurization of the working chamber and an evacuation of the return chamber, in a second position provides an equalization of compressed air between the working chamber and the return chamber, and in a third position provides a return stroke by means of the equalized compressed air remained in the return chamber and an evacuation of the working chamber.
- the machine is characterized in that the valve is enclosed in an end of the cylinder and comprises an inlet channel for pressurization of the working chamber and a bypass channel for evacuation of the return chamber at the same time as the working chamber is pressurized, and a cross channel for providing an interconnection of the working chamber and the return chamber thereby equalizing the pressure of the two chambers at the same time as the inlet and the outlet is blocked by the valve piston, and in that the return chamber communicates with the valve of the cylinder end over a channel (bore) extending axially in the cylinder wall.
- the working strokes thereby are executed in four reciprocal steps, with full pressure in a first step, with about 50% force in a second step ( 1 st return step), with only about 25% in a third step (2nd working step) and with about 1 2.5% in a fourth step (2nd return step).
- FIG. 1 diagrammatically illustrate the method according to the invention in a 3-step method including equalization of the pressure preceding the return stroke.
- Figures 2a-2g correspondingly illustrate a 7-step method comprising three successive pressure equalization steps (2b, 2d, 2f).
- Figure 3 shows the markings which are used for explanatory purposes in figures 1 and 2.
- Figure 4 shows a piston-cylinder unit according to the invention having means for accurately indicating the position of the piston in the cylinder.
- Figure 5 shows an axial cross section through a piston-cylinder unit which is suited for use in the methods according to figures 1 and 2.
- Figure 6 is a cross section view, in an enlarged scale, along line VI-VI of figure 5.
- Figure 7 is an enlarged scale view of the left hand part of the cylinder of figure 5.
- Figure 8 is a cross section view along line VIII-VIII of figure 5.
- Figure 9 diagrammatically shows a valve structure for use in a pneumatic machine according to the invention and arranged for being mounted in an end of the piston cylinder unit.
- Figures 10a-10d show four different functional positions of the valve of figure 9.
- Figures 1 1 , 1 2 and 1 3 show a detail, in three different functional positions, of an alternate embodiment of a valve means for a piston-cylinder unit according to the invention, likewise mounted in an end of a cylinder-piston unit.
- Figures 1 a-1 c show a pneumatic machine comprising a cylinder 1 in which a piston 2 is displaceable.
- the piston has a piston rod 3 projecting out from the cylinder.
- the cylinder is formed with a connection 4 for compressed air entering a working chamber 5 of the pneumatic machine, and a second connection 6 leading to a return chamber 7 thereof.
- the two connections 4 and 6 are connected to a step valve 8 which can take three different positions of function, which are illustrated in figures 1 a-1 c, respectively.
- the valve 8 is connected to a source of compressed air.
- the valve may be of linear type, but in the drawings the valve is shown as a rotary valve. It is evident that the working chamber in the position according to figure 1 a is under full pressure, whereas the return chamber 7 is evacuated.
- valve 7 When the piston 2 approaches the end position of its working stroke the valve 7 is rotated by 1 20° to the position shown in figure 1 b. In this position the supply of compressed air is broken, and the working chamber 5 and the return chamber 7 are connected to each other over a shunt conduit 9, whereby the air pressures of the two chambers are being equalized. By a rough approximation it can be said that the pressure is distributed by 50% in each of the two chambers 5 and 7.
- valve 8' is formed as a 7-step valve.
- the function with the pressure equalization between the working chamber 5 and the return chamber 7 is basically the same as that of figures 1 a-1 c, but the function comprises three successive pressure equalization steps, which are shown in figure 2b (to about 50%), 2d (to about 25%) and 2f (to about 1 2.5%).
- FIG 2a the piston 2 is pressed by full force in a first working stroke in the working chamber 5; in figure 2b there is provided a first pressure equalization between the working chamber 5 and the return chamber 7; in figure 2c there is shown a first return stroke by means of the about 50% pressure which is remained in the return chamber 7; in figure 2d a second pressure equalization is obtained to about 25% pressure; in figure 2e there is obtained a second working stroke or damping stroke by means of the 25% the air pressure remained in the working chamber 5; in figure 2f there is obtained a third pressure equalization to about 1 2.5% of the original pressure; and in figure 2g there is shown a second return stroke by means of the presently strongly reduced air pressure.
- the piston-cylinder unit shown in figure 4 is formed with a positioning means for the piston, which is directly connected to a step feeding means (not shown in figure 4) for the step valve 7.
- the cylinder 1 is star-formed having eight star tops 1 0, all having axially through bores 1 1 .
- Four of said bores are used for through mounting bolts, and one or more of the remaining bores are used for transmitting compressed air axially through the cylinder, in particular in the cylinder of the type shown in figure 5, in which case there is only a single connection for compressed air provided at one end of the pneumatic machine.
- the right hand end 1 2 of the cylinder shown in figure 4 has an end bore for the piston rod 3 and it is also formed with a cavity 1 3 over which the return chamber 7 directly communicates with the uppermost air bore.
- the left hand cylinder end 14 has a corresponding cavity 1 5 through which it communicates with the bore 1 1 .
- the belt extends, well protected, through one of the bores 1 1 of the cylinder 1 .
- One of the pulleys 1 7 may be a tooth gear which can be mounted on a shaft which at the free end thereof has a positioning means having a great many bars, magnetic code dots or similar marking which can be read by a position reader which in figure 4 is marked as a reader pin extending out through the left end 1 4. Said position reader thereby very accurately gives the position of the piston and can, as mentioned above, be connected to the valve thereby making the piston turn direction at very accurate positions in the cylinder.
- the piston-cylinder unit shown in figure 5 has a compressed air connection 1 8 only at one end thereof, which connection enters the left hand end of the cylinder, in which a several step valve 1 9 is housed.
- Said valve may be of the type shown in figures 9 and 1 0.
- the compressed air enters the working chamber 5 over one of the axial bores of the cylinder and through a cross bore 20 in the inner cylinder wall of the cylinder.
- Said axial bore is plugged so as to avoid escaping of air therefrom.
- Another one of said axial bores 44 is formed as a connection between the return chamber 7 and the valve 1 9, and at the left end of the cylinder said bore is connected to the valve 1 9 over a channel or bore 21 .
- the axial bore 44 is connected to the return chamber 7 over a cross bore 22 in the inner cylinder wall.
- the pneumatic machine can operate over only one compressed air connection 1 8, which makes it possible to use the machine in narrow spaces where it has until now often not been possible to make use of pneumatic machines.
- the piston is, at both ends inside the cylinder, formed with damping pistons co-operating with damping cavities in the cylinder ends.
- the rotary valve 1 9 at the left end of the piston-cylinder unit of figure 5 is more closely described in connection to figure 9.
- the valve is a specific function valve 23 arranged for controlling the function of a single acting pneumatic machine according to the invention - without the need of using a return spring or another type of similar means.
- the valve 23 preferably is mounted at one end of the cylinder and it is formed with two valve discs, a lower valve disc 24 which is stationary mounted, and an upper valve disc 25 which is rotatable on the stationary valve disc 24 operated by a pin 26.
- the stationary disc 24 is formed with four connections, a compressed air connection 27, an evacuation connection 28, a connection 29 leading to the working chamber of the cylinder, and a connection 30 to the return chamber of the cylinder.
- the upper valve disc 25 is likewise formed with four connections 31 , 32, 33 and 34 which are arranged like in the bottom disc 24. Between the connections 31 and 32 there is a first bypass channel 35, and between the connections 33 and 34 there is a second bypass channel 36.
- the compressed air connection 27 is formed with a one way valve 37 which allows a flow of air only into said connection 27.
- a one way valve 38 allowing a flow of air only in the direction from 31 to 32; in the bypass channel 36 there is likewise a one way valve 39 allowing flow of air only from 33 to 34; also there is a first bypass channel 40 between the working chamber connection 29 of the lower disc 24 and the connection 31 of the upper disc 25 and a second bypass channel 41 between the connections 28 and 32.
- the valve makes it possible to utilize the equalization pressure as a power for the return stroke of the piston.
- valve 23 is shown in its closed position.
- the compressed air connection 27 is closed, the return chamber connection 30 is closed and the working chamber connection 29 is evacuated over channels 29-40-38-41 -28.
- Figure 1 0a shows the working stroke of the cylinder, in which case the upper valve disc 25 is rotated by 45°. Compressed air is supplied to the working chamber over the connections 27-33-39-34-29, and the return chamber is evacuated over 30-31 -35-32-28.
- Figure 1 0b shown an intermediate position, in which the upper disc 25 temporarily has been rotated 90° in relation to the lower disc 24.
- the piston movement is damped in the cylinder chambers depending on the compressibility of the air and by means of the damping pistons indicated for instance in figure 5.
- Figure 1 0c shows a position in which the upper disc 25 is rotated another 45° ( 1 35° in total) and in which position the pressures of the cylinder chambers 5 and 7 are equalized over 29-33-36-30-34.
- the compressed air connection 28 is closed by the non return valve 38.
- the return stroke is made in that the working chamber 5 is evacuated by 29-40-31 -35-32-41 -28. Thereby a complete working cycle has come to an end, and a new cycle is started according to figures 1 0a-1 0d.
- the cylinder can be formed with an axially operating valve which is enclosed in one end of the cylinder, as shown in figures 1 1 -1 3.
- the cylinder is formed with only a single compressed air connection 42
- the piston-cylinder unit is formed with a valve enclosed in one end 45 of the apparatus, which valve connects and disconnects the compressed air, respectively.
- Figures 1 1 -1 3 are fragmentary axial cross section views through one end of a piston-cylinder unit giving a strong working stroke actuated from the working chamber 5 and a softer return stroke actuated from the return chamber 7.
- both the compressed air inlet 42 and the compressed air outlet 43 are formed in the same cylinder end.
- the flow of air from the working chamber 5 to the return chamber 7 goes through one of the axial bores 44 of the cylinder.
- the end 45 of the cylinder is formed with a valve piston 46 and with a system of channels 47, 48 which both allow a supply of compressed air to the working chamber 5 through the inlet 42 and an evacuation of the return chamber 7 through the outlet 43.
- the cylinder end 45 is formed with a first channel 47 connecting the compressed air inlet 42 to the working chamber 5 and a second channel 48 connecting the return chamber 7 to the outlet 43 via the cylinder bore 44.
- the valve piston 46 is slideable in the a valve chamber 49 in the end of the cylinder, and said valve piston can take two main positions, namely a pressure position which is shown in figure 1 1 and an evacuation position which is shown in figure 1 3.
- the valve piston is pressed towards a non- pressurized position by a spring 50.
- the valve piston also is formed with a transverse channel 51 which, in an intermediate position of the valve piston, interconnects the working chamber 5 with the return chamber 7, as shown in figure 1 2, whereby the pressure is equalized between said two chambers 5 and 7.
- the valve piston 46 blocks the pressure channel 47. This intermediate position is taken under only a very short moment of the return stroke of the valve piston.
- the valve piston 46 also is formed with a bypass channel 52 allowing an evacuation of the return chamber 7 while the valve piston is in pressurized condition.
- FIG 1 1 the compressed air inlet 42 is shown pressurized, whereby the compressed air forces the valve piston 46 to the right (as shown in the drawings), and compressed air is thereby supplied to working chamber 5; at the same time the return chamber 7 is evacuated over the cylinder bore 44 and the bypass channel 52, and the working piston can be moved freely to the right during its working stroke, as shown in figure 1 1 .
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
- Pipeline Systems (AREA)
- Yarns And Mechanical Finishing Of Yarns Or Ropes (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Actuator (AREA)
Abstract
Description
Claims
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AU12148/97A AU717444B2 (en) | 1996-11-13 | 1996-11-13 | An apparatus for reducing the consumption of compressed air in pneumatic machines |
PCT/SE1996/001467 WO1998021487A1 (en) | 1996-11-13 | 1996-11-13 | An apparatus for reducing the consumption of compressed air in pneumatic machines |
CA002271114A CA2271114A1 (en) | 1996-11-13 | 1996-11-13 | An apparatus for reducing the consumption of compressed air in pneumatic machines |
EP96943412A EP0934467A1 (en) | 1996-11-13 | 1996-11-13 | An apparatus for reducing the consumption of compressed air in pneumatic machines |
BR9612784-8A BR9612784A (en) | 1996-11-13 | 1996-11-13 | Pneumatic machine. |
JP52244498A JP2001503839A (en) | 1996-11-13 | 1996-11-13 | Devices for reducing the consumption of compressed air in pneumatic machines |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/SE1996/001467 WO1998021487A1 (en) | 1996-11-13 | 1996-11-13 | An apparatus for reducing the consumption of compressed air in pneumatic machines |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1998021487A1 true WO1998021487A1 (en) | 1998-05-22 |
Family
ID=20402239
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/SE1996/001467 WO1998021487A1 (en) | 1996-11-13 | 1996-11-13 | An apparatus for reducing the consumption of compressed air in pneumatic machines |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP0934467A1 (en) |
JP (1) | JP2001503839A (en) |
AU (1) | AU717444B2 (en) |
CA (1) | CA2271114A1 (en) |
WO (1) | WO1998021487A1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7073631B2 (en) * | 2001-07-04 | 2006-07-11 | Robert Bosch Gmbh | Lifting device with synchronization mechanism |
ES2310460A1 (en) * | 2006-11-21 | 2009-01-01 | Festo Pneumatic, S.A.U. | Cylinder pneumatic linear actuator of simple effect. (Machine-translation by Google Translate, not legally binding) |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3211232A1 (en) * | 1981-03-26 | 1982-11-18 | Rexnord Inc., 53201 Milwaukee, Wis. | ENERGY-SAVING METHOD FOR OPERATING A PISTON-CYLINDER COMBINATION AND DEVICE FOR IMPLEMENTING THE METHOD |
-
1996
- 1996-11-13 JP JP52244498A patent/JP2001503839A/en active Pending
- 1996-11-13 EP EP96943412A patent/EP0934467A1/en not_active Withdrawn
- 1996-11-13 CA CA002271114A patent/CA2271114A1/en not_active Abandoned
- 1996-11-13 WO PCT/SE1996/001467 patent/WO1998021487A1/en not_active Application Discontinuation
- 1996-11-13 AU AU12148/97A patent/AU717444B2/en not_active Ceased
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3211232A1 (en) * | 1981-03-26 | 1982-11-18 | Rexnord Inc., 53201 Milwaukee, Wis. | ENERGY-SAVING METHOD FOR OPERATING A PISTON-CYLINDER COMBINATION AND DEVICE FOR IMPLEMENTING THE METHOD |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7073631B2 (en) * | 2001-07-04 | 2006-07-11 | Robert Bosch Gmbh | Lifting device with synchronization mechanism |
ES2310460A1 (en) * | 2006-11-21 | 2009-01-01 | Festo Pneumatic, S.A.U. | Cylinder pneumatic linear actuator of simple effect. (Machine-translation by Google Translate, not legally binding) |
Also Published As
Publication number | Publication date |
---|---|
JP2001503839A (en) | 2001-03-21 |
EP0934467A1 (en) | 1999-08-11 |
AU1214897A (en) | 1998-06-03 |
CA2271114A1 (en) | 1998-05-22 |
AU717444B2 (en) | 2000-03-23 |
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