METHOD AND VALVE APPARATUS FOR CONTROLLING A RECIPROCATABLE FUID ACTATED POWER MACHINE

Abstract: A method and an apparatus for controlling the function of all kinds of reciprocatable power machines which are actuated by means of a pneumatic, hydraulic of any other pressure fluid, irrespective if the machines are of rotary or axially operating type, in which the active power stroke is accomplished using full power of pressure fluid against a reciprocatable piston (2) in the active air pressure chamber (10, 12), and in which the reversing of the direction of operation is made by alternatingly supplying pressure fluid to the opposite air pressure chamber (12, 10) of the machine, said valve comprises a valve poppet (6) having several channels providing means (7) for alternatingly placing one of the pressure chambers (10, 12) of the reciprocatable fluid actuated machine (1, 2) under full pressure, means (8) for building up a certain counter pressure in a pressure chamber which is, at the actual moment, inactive, and means (9) for evacuating the pressure from an inactive pressure chamber of the fluid actuated machine.

Description: METHOD AND VALVE APPARATUS FOR CONTROLLING A RECIPROCATABLE FLUID ACTUATED POWER MACHINE The present invention relates to a method and an apparatus for controlling the function of a reciprocatable fluid actuated power machine. By fluid actuated power machine is meant, in this connection, all kinds of reciprocatable machines which are actuated by means of compressed air, hydraulic oil or any other fluid, irrespective if said machines are of rotatably or axially operating type, and which can execute its power in two opposite directions, or the machine executes its power in one direction only followed by a return movement without power execution, and whereby the reversing of direction is made by reversing the direction of the compressed air or the hydraulic fluid in the active part of the machine. So, the invention is useful both for single acting and double acting reciprocatable fluid actuated power machines. In the following the invention will mainly be discussed in connection to pneumatically operated cylinder-piston units. It is, however, to be understood that this is only illustrative examples which do not restrict the invention. Be it known that the invention is as well useful both for linerary operated machines as for rotating machines and for machines operated by compressed air, hydraulic oil or any other fluid. There are three basic problems of known reciprocatable pneumatic and hydraulic machines both of the single acting and of the double acting type, which problems form basis of the present invention. Said problems appear to the same extent both in rotary operating machines as in axially operating, reciprocatable machines, generally referred to as "compressed air cylinders" or "hydraulic cylinders", but for the sake of simplicity, as mentioned above, the invention will be described in the following only with reference to a pneumatic piston/cylinder unit of reciprocatable type. All three different main problems, which appear in reciprocatable, pneumatic power machines, are related to the reversing phase, during which phase the active part of the machine, in the described case the compressed air piston, is to reverse its direction of operation. This is made in that the compressed air is switched from having acted on one side of the piston to acting against the opposite side of the piston. When reversing the direction of function in previously known apparatus the compressed air is evacuated from the side of the piston which is the active side until the moment of reversal in that the pressurised working chamber is evacuated at the same time as compressed air is supplied to the opposite side of the piston: 1 ) firstly, this makes the often very strongly compressed air pressure at the unloading phase create an air blow which is apprehended as an oftenly very high sound bang, which can be very disturbing; 2) secondly, depending on the momentary draining of the pressure in the air chamber which has so far been pressurised some amount of compressed air gets lost; such loss of compressed air means a economical loss of value considering the costs and the work for producing said compressed air; 3) thirdly, at the same time as one of the compressed air chambers is being evacuated and the opposite compressed air chamber is pressurised by means of the oftenly high air pressure the piston is immediately or momentarily stopped and momentarily thereafter starts moving in the opposite direction with high speed and high power. This may in some cases cause problems. Said problem also appears in hydraulically operated machines. Still another problem in pneumatic power machines is to have the active part thereof, generally the piston, stop in a predetermined position. A main reason for this problem is the compressibility of the air. In single acting reciprocatable cylinders the power stroke is made by means of compressed air, whereas the return movement is generally accomplished by means of return spring. In order to overbridge the power of the return spring it is necessary to make use of a substantially stronger power of the compressed air or the hydraulic fluid than would have been needed if the cylinder had no return spring. The object of the invention therefore is to eliminate all of the above mentioned problems and disadvantages by suggesting a simple method and a simple type of valve arrangement, and thereby to suggest a method and an apparatus in a reciprocatable, single or double acting fluid actuated power machine: a) which to a high extent reduces the noise which is created at the evacuation of the air pressure when the active part of the power machine reverses its operation direction; b) which makes it possible to save at least 30-50% of compressed air of the previously needed amount of fluid; c) which makes the active part of the pneumatic or hydraulic power machine both stop and start relatively softly during the reversing phase; d) and which makes it possible to stop the piston movement rather exactly at any point of the piston/cylinder unit. According to the invention this is generally accomplished in that the piston of the fluid actuated machine meets a counter pressure both at the end of an active power stroke and at starting of a power stroke in the opposite direction. The soft braking preferably is made in that the two sides of the fluid actuated machine are interconnected over a shunt shortly before the active part of the machine (the piston) reaches the end of its active stroke whereby the piston softly becomes braked. The shunting, or the equalization of the compressed air can be made in several successively increased stages, using mechanical or other types of pressure restricting valves to complete equalization of power at both sides of the piston. In a double acting cylinder the function of the piston, during the reversing of the working direction is split into eight different phases, namely, starting from a full speed working phase in one direction: A. a full speed working phase in a first direction (→), during which the piston is moved in a predetermined direction (e.g. as shown in figure 1 ); B. a soft stopping phase (figure 2) during which the piston movement is softly braked to stop; C. an equalizing and reversing phase (figure 3), during which the two pressure chambers are subjected to the same pressures; D. a soft starting phase (figure 4) during which the piston starts moving in the opposite direction ( -) against a slight counter pressure which is successively reduced to atmospheric pressure; E. a full speed working phaseffigure 5) at full pressure in said opposite direction ( -) ; F. a soft stopping phase (figure 6) during which the piston movement is softly braked to stop; G. an equalizing and reversing phase (figure 7), during which the two pressure chambers are subjected to the same pressures; H. a soft starting phase (figure 8) in a reversed direction during which the piston starts moving in said first direction (→) against a slight counter pressure which is successively reduced to atmospheric pressure. The function is illustrated in the following table 1 : T A B L E 1 (reversible power type) shown left right actual phase in chamber chamber function next phase fig. nr pressure (P) pressure (P) of the phase A 1 full P 0 full speed → soft stopping → B 2 full P choking 1 soft stopping → stop/reverse C 3 0 0 stop/reverse z> soft starting <- D 4 choking t full P soft starting - full speed <- E 5 0 full P full speed <- soft stopping <- F 6 choking ■ I full P soft stopping - stop/reverse <rz G 7 0 0 stop/reverse c soft starting - H 8 full P choking t soft starting - full speed → In a single acting pneumatic cylinder the above mentioned shunt power can, according to the invention, be used as a return power for the piston by draining the power of the former pressure side. To this end there is used a four-stage valve means having four positions providing five functional phases. The function thereof is illustrated in the following table 2: T A B L E 2 (single acting power type) Now the invention is to be described in detail with reference to the accompanying drawings, in which figures 1 - 8 show a sequence of the above mentioned eight functional phases for a double acting, reciprocatable pneumatic machine, in which figure 9 diagrammatically illustrates a rotatable valve for performing the soft stopping and soft starting function of the pneumatic or hydraulic power machine, and in which figure 10 illustrates pictures used for marking of the three pressures in figures 1 - 8. Figure 1 1 is a diagrammatical view of a 4-stage valve for performing the operation of a single power operation pneumatic machine, and figures 12-15 diagrammatically illustrates the function thereof. Figures 16-18 illustrate an example of a pneumatic piston-cylinder unit for executing the method illustrated in figures 12, 14 and 15, respectively. The operation method of a reversible type power pneumatic or hydraulic piston-cylinder of the invention is explained in connection to the figures 1 -9 of the accompanying drawings, which diagrammatically show a piston/cylinder unit comprising a cylinder part 1 and a piston part 2 having a piston rod 3, connections 4 and 5 for a pneumatic or hydraulic pressure fluid at each end of the cylinder 1 , and a valve 6 for creating the various functional phases of the apparatus. The valve 6, which in the illustrated case is of rotatable type, but which may as well be of axially reciprocatable type, is formed with a pressure distributing means 7, a means 8 for providing a choking or a shunting of the pressure chambers of the power machine, for instance the piston-cylinder unit, valve, and a means 9 for evacuating the pressure chambers of the cylinder 1 , 2. The valve is illustrated only with respect to the function thereof in figures 1-9, be it obvious to the expert how to design the valve in order to obtain such functions. During its operation the valve of figures 1 -9, in the illustrated case can take eight different active positions marked with letters A - H in figures 1 -8 respectively. A. Working phase (direction =>), shown in figure 1 : We have chosen to start the description of the function in a valve position (fig. 1 ) in which the piston chamber 10 at the stationary mounted side 1 1 of the cylinder 1 is under full working pressure. The pressure fluid connection 4 at said stationary end of the cylinder, is connected the pressure distribution means 7 of the valve 6 placing the outer piston chamber 10 is under full pressure. The piston (rod) chamber 12, which is now inactive, is drained in that the pressure fluid connection 5 at said side of the cylinder is open to the ambient via the evacuation means 9. The piston 2 is thereby forced with full power to the right as shown in figure 1 . B. Soft stopping (equalization, direction =>) phase, figure 2: After the valve 6 has been rotated a certain step (45° as illustrated in the drawings) in the clockwise direction, as shown in figure 2, the pressure fluid connection 4 is still under full pressure from the pressure distributing means 7. When the piston 2 approaches the piston rod end of the cylinder a counter force is applied to the piston rod chamber 12. There are basically two methods of providing such counter force: a) to apply a slight air or hydraulic pressure in the piston rod chamber 12 from the choking means 8, which pressure is stepwise or successively decreased, and concurrently therewith stepwise or successively decreasing the pressure in the outer piston chamber 10 so that the piston 2 is softly brought to stop; b) for use in pneumatic machines, to break the air pressure to the outer piston chamber 10 and immediately thereupon to open a bypass or shunt 13 (marked with dotted lines in figure 2) between the outer piston chamber 10 and the piston rod chamber 12, whereby the pressure from the outer piston chamber 10 is distributed with equal force also to the piston rod chamber 12, whereby there is an equalization of pressure in said two chambers 10 and 12 and the piston 2 is softly brought to stop. C. Inverting phase (direction =)), figure 3: In this third phase the valve 6 has rotated (45°), whereby both the outer cylinder chamber 10 and the piston rod chamber 12 are being blocked or are opened to the ambient over the evacuation means 9. Now the piston 2 is balanced from both sides and is ready to start moving in the opposite direction. D. Soft starting phase (direction =), figure 4: The outer piston chamber 10 a) is connected to the choking means 8, whereby said chamber is closed and is thereupon stepwise or successively opened to the ambient, whereas the piston rod chamber 12 is subjected to full pressure, and this makes the piston start moving with a softly accelerated piston movement. Alternatively b) the piston chamber can be put under a slight, stepwise or successively decreased counter pressure over the choking means 8. In both cases the piston rod chamber 12 is connected to the pressure distributing means 7 supplying full pressure to the piston rod chamber 12. The pressure of the piston rod chamber 12 is higher than the pressure of the outer piston chamber 10, and the piston softly starts moving to the left, as shown in figure 4. The pressure gradient is stepwise or successively increasing to maximum pressure following the decrease of the choking pressure in the outer pressure chamber 10. E. Working phase (direction <=), figure 5: In this fifth phase the valve poppet 6 has rotated so that the cylinder chamber 12 is put under full pressure over the pressure means 7, and the outer piston chamber 10 is drained to the ambient, whereby the piston moves at full pressure and full speed to the left. F. Soft stopping phase (direction <=), figure 6: In this phase the same process as that of point B above is repeated, but with the piston moving in the opposite direction. The outer piston chamber 10 is connected to the choking means 8, or the pressure of the piston rod chamber 12 is distributed to the outer piston chamber 10. Thereby the piston 2 is softly brought to stop. G. inverting phase (direction cz), figure 7 In this phase the same process is repeated as that of step C above but with the piston being prepared for moving from left to right (cz). H. Soft staring phase (direction cz), figure 8: In this phase the same process is repeated as that of step D above but with the piston softly staring to move to the right as shown in figure 8. Thereby a complete operation cycle is ended and the cycle is repeated from point A above. In figure 9 in indicated that the valve 6 can be connected to a motor 14, which can be an electrical or pneumatical motor, for instance a stepping motor and which can operate the cylinder-piston unit successively until the operation is to cease. The stepping motor can be arranged to provide any desired number of small steps, e.g. from 10-200 steps per 360° rotation. The valve can be rotated stepwise or continuously and by different speeds depending on what function is desired from the cylinder-piston unit. By choking of breaking the pressure supply to the piston chambers 10, 12 it is also possible to make the piston 2 stop and remain still standing in any position in the cylinder 1 between the end positions, thereby avoiding such "creeping" which can generally not be avoided in pneumatic machines of conventional type. In pneumatical power machines it is often difficult to stop the working movement in a predetermined position for the piston, among other things depending on the compressibility of the air. According to the invention this problem is solved in a pneumatic or hydraulic apparatus or the above described type in that the deceleration and the stopping of the piston movement is made in several successive steps with successively or stepwise reduced pressure differences between the working side of the piston and the evacuated side of the piston. This can simply be made by forming the valve means so as to successively or stepwise choke the evacuation of the evacuated side of the piston, for instance by a choking in four or more steps, like from 100% to 50% to 25% to 0% pressure choking. Said choking can be accomplished in various ways, as obvious to the expert, for instance in that evacuation bores or pressure restriction valves be provided in the valve poppet in such positions and are formed such as to successive or stepwise choking of the piston, staring when the piston has reached a certain position in the cylinder. Thus, a first choking can be provided to 50% pressure difference between the two piston chambers 10, 12 when there is only about 50 mm left of the piston race, a second choking to 25% pressure difference when there is 10 mm left of the piston race, and a choking to 0% pressure difference when there is only one or two mm left of the piston race. The said last mentioned "choking step" follows as an addition step after the working phases according to figures 2 and 6. In figure 11 there is diagrammatically shown a 4-stage valve 15 which is mainly useful for controlling the operation of single power operated pneumatic machines, like cylinder-piston units. The 4-stage function, including the air return movement is shown in figures 12-15. Conventional pneumatical cylinders of this type generally are formed with a return spring means, at the piston rod chamber side, which makes the piston return to the stationary side of the cylinder after having performed a working phase. The present valve, which can be mounted at the end of the cylinder, or elsewhere, provides a function eliminating the need of a return spring as used in conventional one power stroke pneumatic cylinders. The valve is formed with two discs, a bottom disc 16 and a top disc 17. The bottom disc 16 is stationary and the top disc 17 is rotatable over a pin 18 in relation to the bottom disc. The bottom disc is formed with four connections, an air pressure power supply connection 19, a draining supply connection 20, a connection 21 to the outer piston chamber and a connection 22 to the piston rod chamber. The top disc 17 is likewise formed with four connections 23, 24, 25 and 26 provided similarly to the bottom disc connections. Between the connections 23 and 24 there is a bypass 27, and between the connections 25, 26 there is a bypass 28. The supply connection 19 is formed with a one-way valve 29 allowing flow of fluid only into said connection. In the bypass 27 there is a one-way valve 30 allowing flow of fluid only in the direction 23 to 24, and in the bypass 28 there is a one-way valve allowing flow of fluid only in the direction 25 to 26. Further there is a bypass first 32 between the outer piston chamber connection 21 in the bottom disc 16 and the connection 23 of the top disc 17 and a second bypass 33 between the connections 20 and 24. The valve 15 makes is possible to make use of an equalization pressure as piston return power. Also in this embodiment there is a soft stopping function and a soft starting function. The function is the following: Complete stop, figure 11 With the valve discs 16, 17, as shown in figure 1 1 there is no supply of power from the connection 19; the piston rod connection 5 is closed, and the outer piston chamber connection 4 is drained. Power stroke, figure 12 After rotating the top disc 16 (in this case 45°) the power the top connection 25 is in flight with the supply 19, and the top connection 26 is in flight with bottom disc connection 21 . Thereby compressed air is - by a successively or stepwise increased pressure gradient - supplied to the outer piston chamber 4 via the bypass 28. The piston rod chamber 5 is open to the ambient over the connections 22, 23, 24 and 20 via the bypass 27. Intermediate stop position, figure 13 At the end of the power stroke the top valve disc 17 is momentarily rotated to the position shown in figure 3, whereby the all bottom connections and top connections are separated from each other. The piston movement is thereby slightly dampened depending on the compressibility of the air in the cylinder chambers 4 and 5. The said intermediate stop position follows during a very short period of time, for instance only a few parts of a second. Equalization position, figure 14 After a very short while the top disc 17 is rotated to the position shown in figure 14, in which position the power supply 29 is blocked by the one-way valve 30 in the bypass 27; the drain connection 20 is open to the ambient; the outer cylinder chamber 4 is directly connected to the piston rod chamber 5 over the connections 21 , 25, the bypass 28 and the connections 26, 22. Thereby the pressure from the outer piston chamber 4 is distributed also to the piston rod chamber 5, and the piston movement is thereby softly brought to stop. A pressure equalization is obtained between the two piston chambers 4 and 5. Return stroke, figure 15 After rotating the top disc 17 another step (45°) the situation appears which is shown in figure 15, and in which the outer piston chamber 4 is opened to the ambient over the bottom disc connection 21 , the bypass 32, the top disc connection 25, the bypass 28, the top disc connection 26 the bypass 33 and the drain connection 20. The piston rod chamber 5, which is blocked by the top disc connection 22, is still under the part pressure obtained during the equalization step. Said pressure is sufficient for returning the piston to its original position adjacent the stationary end of the cylinder. Therefore the piston softly starts moving to the right, as shown in figure 15. The pressure successively decreases in the piston rod chamber 5 following the advancement of the piston, and as a consequence the return speed of the piston successively decreases thereby providing a soft stopping of the piston adjacent the stationary end of the cylinder. Thereby a complete operation cycle has come to an end. Figures 16-18 are fragmentary cross section views in the axial direction of one end of a piston-cylinder unit for executing the single power stroke as illustrated in figures 12, 15 and 15, respectively. In the illustrated piston-cylinder unit both inlet and outlet of air is arranged at the same end of the piston. The flow of air from the piston rod chamber 12 goes through channels 34 at the periphery of the cylinder 1 . The end head 35 of the cylinder is formed with a valve poppet 36 and with a passageway system 37, 38 allowing both inlet of pressurised air, at inlet 4, into the piston chamber 10 and outlet of from the piston rod chamber 12, through outlet 5. The end head 34 is formed with a first passageway 37 communicating the air inlet 4 with the piston chamber 10 and a second passageway 38 communicating the piston rod chamber 12 with the outlet 5 over the peripheral channel 34. The valve poppet 36 is slidable in a cylinder chamber 39 in the head 35 and can take two different main positions, a pressure position shown in figure 16, which corresponds to the valve position of figure 12, and a non-pressure position which is shown in figure 18, and which corresponds to the valve position of figure 15. The valve poppet 36 is biassed by a spring 40 towards its non-pressurised position. The valve poppet is also formed with a cross channel 41 which in an intermediate position of the valve poppet 36 communicates the main piston chamber 10 with the piston rod chamber 12 thereby balancing the air pressure between said two chambers 10 and 12. In said intermediate position the valve poppet 36 blocks the pressure channel 37 and the drain channel 38. This intermediate position, which is taken during a very short moment of the return stroke of the valve poppet 36 is shown in figure 17. This situation corresponds to the valve setting shown in figure 14. The valve poppet 36 also is formed with a bypass channel 42 allowing a draining of the piston rod chamber 12 in the pressure position of the valve poppet 36. In figure 14 is shown that the inlet 4 is pressurised. The air pressure forces the valve poppet 36 to the right, whereby compressed air is supplied to the main piston chamber 10; at the same time the return channel 34 from the piston rod chamber 12 is communicated with the bypass channel 42, and the piston 2 is freely moved to the right corresponding to the valve setting shown in figure 12. After the piston 2 has been stopped softly at the end of its stroke and there is no pressure in the inlet 4 or the outlet 5 the spring 40 forces the valve poppet 36 back towards its base position. While moving to the left the cross channel 41 connects the air passageways between the two chambers 10 and 12 to each other for a short moment, as shown in figure 17. The former air pressure in the main chamber 10 is thereby transmitted to the piston rod chamber 12 over the cross channel 41 , part of the end head passageway 38 and the "return" channel 34. In this position both the inlet 4 and the outlet 5 are blocked by the valve poppet. When the valve poppet 26 has been return to its initial position, as shown in figure 18 the air pressure in the main chamber 10 is drained over the passageway 37, the cross channel 41 and the outlet 5. The "balanced" pressure still existing in the piston rod chamber 12 is sufficient for softly forcing the piston 2 back to its starting position adjacent the end head 35. Thereby a complete operation cycle is ended. Like in figures 1 1-15 there is no need for a return spring or any other means for returning the spring in the illustrated one-way power pneumatic cylinder-piston unit. Reference numerals 1 cylinder part 23 top disc connection 2 piston part 24 top disc connection 3 piston rod 25 top disc connection 4 air connection 26 top disc connection 5 air connection 27 bypass 6 valve 28 bypass 7 pressure distribution means 29 one-way valve 8 choking means 30 one-way valve 9 evacuation (equalization) means 31 one-way valve 10 outer piston chamber 32 bypass 1 1 valve outlet 33 bypass 12 air cylinder connection 34 "return" channel 13 bypass, shunt 35 end head 14 motor 36 valve poppet 15 valve 37 passageway 16 bottom disc 38 passageway 17 top disc 39 end head chamber 18 pin 40 spring 19 power supply connection 41 cross channel 20 drain connection 42 bypass channel 21 outer piston chamber 22 piston rod chamber

Claims: C L A I M S 1 . A method of controlling the function of all kinds of reciprocatable power machines which are actuated by means of a pressure fluid (pneumatic, hydraulic etc.), irrrespective if the machines are of rotary or axially operating type, in which the active power stroke is accomplished using full power of pressure fluid against a reciprocatable piston in the active pressure chamber, and in which the reversing of the direction of operation is made by alternatingly supplying pressure fluid to the opposite pressure chambers of the machine, characterized in that the stopping and/or the starting of the active power stroke of the reciprocatable power machine is made in that a certain counter pressure is built up in the inactive chamber of the reciprocatable machine, so that the power of the pressure fluid in the active air chamber is at least partly counter-acted thereby obtaining a soft stopping and/or a soft starting of the piston movement of the fluid actuated power machine. 2. Method according to claim 1 , characterized in that the counter-acting pressure fluid in the inactive pressure chamber is stepwise or successively decreased, beginning a short distance before the piston reaches the end of its stroke, for instance from a position where the piston has reached about 95% of its stroke and in several successive steps, for instance corresponding to 95%, 98%, 99,5% and 100% of the piston stroke, until said inactive pressure chamber is opened to the ambient, for instance by reducing the pressure differences between the active and inactive air chambers ( 10, 1 2) in several steps like to 50%, 25% and 0% pressure differences. 3. A method according to claim 1 or 2, characterized in that the previously fully pressurised working chamber (10) is only partly evacuated (figure 4) before the opposite, now active working chamber (12) is placed under full working pressure (figure 5), or the previously pressurised working chamber (10), which after having been evacuated by being placed under atmospheric pressure, is closed a short moment (figure 4) while the opposite working chamber (12) is placed under full working pressure, whereupon the first mentioned working chamber (10) is evacuated (figure 5) . 4. A method according to any of the preceding claims, characterized in that the pressures of the pressure chambers (4, 5) of the double acting fluid actuated power machine are equalised before the working direction is reversed. 5. A method according to claim 4, characterized in that the opposite pressure chambers (10, 12) are connected to each other before the pressure of the previously fully pressurised working chamber (10) is unloaded by evacuation and the opposite working chamber (12) is placed under full pressure. 6. A method according to claim 4, used in reciprocatable pneumatic power machines, characterized in that the previously fully pressurised working chamber (10 or 12) is evacuated by being opened to the ambient, and in that the part of the equalised air pressure appearing in the opposite working chamber (12 or 10) is used to return the piston to its initial position. 7. A method according to claim 4, used for a one-way power stroke pneumatic cylinder-piston unit, characterized in that the previously pressurised piston chamber (10) is drained and that the balanced air pressure still existing the piston rod chamber (12) is used for returning the piston (2) to its starting position at the outer cylinder end. 8. A valve for executing the method according to any of preceding claims for controlling the function of all kinds of reciprocatable power machines which are actuated by means of a pressure fluid, irrrespective if the machines are of rotary or axially operating type, in which the active power stroke is accomplished using full power of pressure fluid against a reciprocatable piston (2) in the active air pressure chamber (10 or 12), and in which the reversing of the direction of operation is made by alternatingly supplying pressure fluid to the opposite air pressure chamber (12 or 10) of the machine, characterized in that said valve comprises a valve poppet (6) having several channels providing means (7) for alternatingly placing one of the pressure chambers (10 or 12) of the fluid actuated power machine (1 , 2) under full pressure, means (8) for building up a certain counter pressure in a pressure chamber (12 or 10) which is, at the actual moment, inactive, and means (9) for evacuating the pressure from an inactive pressure chamber of the fluid actuated machine. 9. A valve according to claim 8, characterized in that the means (8) for building up a certain counter pressure in a pressure chamber which is, at the actual moment, inactive, comprises a bypass channel (13) for providing an equalization of the pressures in the two working chambers (10, 12) before the power machine is brought to reverse its working direction. 10. A valve according to claim 8, characterized in that the valve is designed so that a double power acting fluid operated power machine in connection to the reversing of the working direction - is firstly subjected to an equalization of the pressures between the working chambers (10, 12), - whereupon the previously pressurised working chamber is evacuated, - the said previously pressurised working chamber is closed a short moment after having been evacuated, at the same time as the opposite working chamber is placed under full working pressure, - and finally the said previously pressurised working chamber (10) is evacuated while maintaining full working pressure in the said opposite working chamber (12). 1 1 . A valve according to claim 8, characterized in that the valve is formed with means to provide a choking of the flow of evacuated pressure fluid successively or stepwise when the piston has moved to a distance close to the end of its stroke, for instance means for choking the evacuation of pressure fluid in four steps corresponding to 50%, 25%, 5% and 0% of the maximum working air pressure. 12. A valve according to claim 8, characterized in that said valve is designed for a pneumatic reciprocatable cylinder-piston units of single power direction type having a non-active return movement for the air piston, thereby - providing an equalization (fig. 14) of the pressures of the two air pressure chambers (4, 5), - an evacuation of the previously fully pressurised air chamber (4), and - using said equalised pressure in the previously non-active air pressure chamber (5) for return moving the piston to its initial position. (Figures 1 1-15) 13. A valve according to claim 12, characterized in that the end (35) of the cylinder is formed with a valve arrangement (36-42) arranged so as to allow the equalised pressure still existing in the piston rod chamber (12) to press the cylinder (2) back to its starting position for the power stroke. (Figures 16-18)

Inventors: HARJU BERT, HARJU, BERT
Applicants: HARJU BERT, POS LINE AB, HARJU, BERT, POS-LINE AB
Application year: 1995
Main classification: F15B11
IPC codes: F15B11, F15B15