EP0455258B1 - Procédé d'opération d'un moteur pneumatique et dispositif pour l'exécution de ce procédé - Google Patents

Procédé d'opération d'un moteur pneumatique et dispositif pour l'exécution de ce procédé Download PDF

Info

Publication number
EP0455258B1
EP0455258B1 EP91107221A EP91107221A EP0455258B1 EP 0455258 B1 EP0455258 B1 EP 0455258B1 EP 91107221 A EP91107221 A EP 91107221A EP 91107221 A EP91107221 A EP 91107221A EP 0455258 B1 EP0455258 B1 EP 0455258B1
Authority
EP
European Patent Office
Prior art keywords
pressure
working
cylinder
pass
chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP91107221A
Other languages
German (de)
English (en)
Other versions
EP0455258A1 (fr
Inventor
Wolfgang Barth
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE19904031324 external-priority patent/DE4031324A1/de
Application filed by Individual filed Critical Individual
Priority to AT91107221T priority Critical patent/ATE87351T1/de
Publication of EP0455258A1 publication Critical patent/EP0455258A1/fr
Application granted granted Critical
Publication of EP0455258B1 publication Critical patent/EP0455258B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B17/00—Reciprocating-piston machines or engines characterised by use of uniflow principle
    • F01B17/02—Engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/04—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft
    • F01B9/047—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft with rack and pinion

Definitions

  • the invention relates to a novel method for driving a pneumatic motor and a device for performing the method.
  • the new method replaces conventional gasoline or diesel engines or all types of internal combustion engines.
  • the invention has for its object to provide a method and an apparatus for performing the method, which has a system with which a much larger power factor than that which was possible with previously known engines can be achieved and with which it is possible to drive energy to use in an economical and effective way.
  • the object is achieved by the characterizing features of method claim 1, further developments being achieved by method claims 2, 3 and 4; the object is also achieved by the characterizing features of claim 5, wherein further refinements are achieved by the features of claims 5 - 10.
  • a table (A) is attached, which gives the percentages of pressure recovery that can be achieved after the start-up procedure has ended during the normal working phase.
  • the method for driving the pneumatic motor and using an energy-saving drive system is that the drive system includes a plurality of, for example, eight working cylinders I-VIII connected in series, as shown in FIG.
  • Each of these series-connected working cylinders I to VI contains, as shown in Fig. 1, a closed pressure expansion space 15, which contains a constant amount of compressed air throughout the working time, the chip pressure applied before the working thrust acts on the sliding piston plate 2, which acts with the Piston rod 5 is detachably connected via a locking lock 6 containing a locking device 3 to the piston rod 5 of the working cylinder which transmits the working power to the connecting rod device.
  • This clamping pressure applied before the working push moves the sliding piston plate after the working push by 50% of its originally opened clamping pressure value 2 by the path length of the expansion with simultaneous work performance.
  • a pressure bypass chamber 16 is arranged in the area below the sliding piston plate 2, which is connected on the one hand to an injection pressure line 27 connected to a compressed air source 29, which is connected via controllable relay valves to the pressure bypassing chamber of all other working pressure cylinders and the on the other hand, is connected to a pressure bypass line 28 connecting the pressure bypass rooms of all working pressure cylinders I-VIII to one another via controllable relay valves, such that the working fluid expanding from the pressure bypass room 16 after the working stroke via the pressure bypass line 28 controllable by relay valves in the individual pressure bypass rooms 16 of the subsequent working pressure Cylinder can be stored (see Table A in this regard) and for re-opening the pneumatic clamping pressure in the pressure expansion chamber 15 partly from the pressure flue which is stored back into the pressure bypass chamber 16 of all subsequent working pressure cylinders dum can be retracted into the pressure bypass chamber 16 via the relay-controlled energy pressure bypass line 28 and the pressure fluid still required for the application of the required clamping pressure
  • the residual pressure of the pressure bypass chamber 16 which is still required is passed into the subsequent container by means of a pressure fluid fed in from the compressed air source 29.
  • the large number of working cylinders connected in series can be used several times in parallel to ensure a continuous crankshaft drive.
  • the table assumes that the storable opening values within the pressure bypass chambers 16 and the missing residual values required for the following working stroke as injection energy after completion of the thrust via a compressor 30 from the free air of the compressed air source 29 and from this via the injection Pressure line can be supplied to the pressure bypass chamber 16.
  • the pressure is diverted from the pressure bypass chamber 16 before the relief takes place at a pressure of 10 bar in the pressure bypass chamber 16 of the subsequent container, which is prepared for work with the full power of 10 bar, with one circulating compressor or several circulating compressors in the form of small compressors 32 for the system can be used.
  • This transfer corresponds to the power after the energy-free pressure circulation or equalization of a maximum of 20% of the energy to be delivered. Only about 1% wear energy is continuously supplied from the open air.
  • the pressure transfer takes place according to Table A from the pressure bypass chamber 16 of the working cylinder 1 in which the working thrust has just been completed, into the pressure bypass chamber 16, for example of the next cylinder III via the energy pressure bypass line 28, in which only the controllable control valves from Pressure bypass chamber 16 of this first working cylinder, in which the working thrust has just been completed, are open to the bypass chamber 16, for example of the next but one cylinder III.
  • the working cylinder has a sliding piston plate 2, which is in contact with the pressure expansion chamber 15, as the working piston, which can be locked by means of a locking means 3 of a locking lock 6 with the piston rod 5 running through a guide 4, with a certain distance below the sliding piston plate 2 a sliding piston plate 9 and one with an upward and in sliding seals and sliding openings 10 through the sliding piston plate 9 extending thrust supports 7 is provided sliding piston plate 11 which is provided with controllable valves c, the pressure evacuation space 16 being closed at the bottom by a lockable piston plate base plate 12, these thrust supports 7 being rigid with the sliding piston plate 11 are connected.
  • the with the sliding piston plate 2 integrally connected guide 4 can be locked by means of a lock 3 '.
  • the sliding piston plate 9 can be replaced by two sliding piston plates 9A and 9B, the upper sliding piston plate 9A being rigidly connected to the cylinder housing 50 of a control cylinder 8 according to FIG. 6, the lower sliding piston plate 9B being connected to the piston rod 52 of a reversible piston 51 of this control cylinder 8 is rigidly connected.
  • the thrust supports extend through all sliding piston plates 9A and 9B, but not through the sliding piston plate 2, but their downward branches 7 'also extend through the sliding piston plate base plate 12, which ensures that the rigid attachment of the sliding supports 7 on the sliding piston plate 11 Displacement of the sliding piston plate 11 no thrust or pressure build-up occurs. All valve, switching and locking systems are controlled electrically.
  • an opening in the sliding piston plate 9a is free, which creates a connection to the atmosphere.
  • FIG. 7 shows a further exemplary embodiment of a control cylinder 41 which can be controlled on one side and is required to carry out the pressure transfer.
  • the sliding piston plate 2 rests continuously on a release ram 38 and presses a pair of scissors 39 which act as an expansion clamp, because the release ram 38 is equipped with a spring 40 with a low spring tension.
  • the plungers 37 are retracted by the displacement of the sliding piston plates 9A and 9B and locked at the top dead center of the opened or contracted sliding piston plates 9A and 9B, the surface pressure of the sliding piston plate 2 on the release stamp 38 decreasing as soon as the sliding piston plate 11 together with its thrust supports 7 is moved vertically upwards after locking.
  • the spreading clamp-type scissors 39 then close and the piston of the pressure ram 37 is locked.
  • the pressure stamp 37 only extends when the pressure in the pressure bypass chamber 16 has dropped to a certain level.
  • the pressure rams 37 are retracted by sliding plate displacement and locked at the top dead center of the retracted sliding piston plates 9A and 9B.
  • the sliding piston plate 11 displaces the sliding piston plate 9B and, after it meets the sliding piston plate 9A, also vertically upwards; then the release die 38 is relieved of pressure, the scissors 39 and locks the stamp 37.
  • the pressure chamber 42 of the unilaterally controllable control cylinder 41 is connected by means of a pressure line to a pressure vessel 43, the volume of which is many times greater than the volume of the pressure chamber 42 in order to prevent a pressure drop in the pressure bypass chamber 16 during the pressure transfer.
  • a pressure feed pipe 13 Opening into the pressure expansion chamber 15, which is connected to the injection pressure line 27 coming from the compressed air source 29.
  • the energy pressure bypass line 28 is connected to the pressure bypass chamber 16 by means of a connecting line 19, a connection connecting piece 17 connecting the space lying between the sliding piston plate 2 and the upper sliding piston plate 9A and the atmosphere being arranged in the lower region of this space in the side wall of each cylinder 1 .
  • the mode of operation and operating mode of the pneumatic motor are as follows:
  • the pressure circulation volume from pressure bypass chamber 16 to pressure bypass chamber 16 is represented with a partly pneumatic internal pressure circulation and partly the pneumatic pressure circulation of the same pressure volume takes place by means of small compressors 32 with a slight pressure increase.
  • the value of the pressure of the pressure expansion volume and the volume itself in the pressure expansion space 15 and its expansion value depend on the power of the engine.
  • This type of pneumatic motor is operated, for example, with an initial load on the area of expansion on the area of the sliding piston plate 2 from 10 bar to 100 cm 2 area.
  • the pressure volume in the pressure expansion chamber 15 is a dm3 at 10 bar.
  • the original clamping force i.e. To maintain the original pressure value of the pressure volume for a new work, a pressure volume of 1 dm3 with a pressure of 12.5 bar, which loads the plate of the sliding piston plate 9 on an area of 80 cm2, is stored in the cylinder in the pressure bypass chamber 16, which has to be renewed Work performance that is prepared in the system connected in series.
  • a pneumatic or hydropneumatic pressure in the control cylinder 8 can be used to control the circumferential torques of the pressure volume and for transferring residual volume pressure within the pressure bypass chambers of the individual cylinders.
  • This pressure can be applied via a hydraulic pump, since it is a residual pressure, or if higher pressures are used to achieve a high work rate, the control system of the control cylinder 8 is operated via a compressor.
  • the pressure present in the control line system according to FIG. 6, which is responsible for the control cylinder 8, is generally always approximately constant, because when the slide piston plate in the control cylinder 8 is shifted, the pressure volume, the volume of which is constant, is bypassed with a small circumferential deviation.
  • the pistons of the control cylinder 8 have an area of 15 cm2.
  • the load on the sliding piston surface 9B is 375 kg per 80 cm2 area.
  • a control pressure of 12.5 bar is applied to the piston of the control cylinder 8 with its 30 cm2 total area, which within the bypassing process of transferring residual pressure in the pressure bypass rooms by means of the intermediate small compressor 32 up to a maximum of 15 bar is increased.
  • the thrust supports 7 have a cross-sectional area of 10 cm2 and in their vertical course in the pressure bypass chamber 16 which has a height of 10 cm, they consequently occupy 200 cm3 of the volume of the pressure chamber.
  • the pressure volume of the pressure bypass chamber is 16 1000 cm3 at a pressure of 12.5 bar.
  • a certain pressure filling quantity is injected in the pressure expansion spaces 15 from the compressor 30 via the pressure injection line 27. It is the same in all pressure bypass rooms 15.
  • the expansion size of the expansion spaces 15 has a different volume within each cylinder before the engine is started up. Therefore, the pressure is lowered at different heights according to the size of the room.
  • 1 dm3 is also filled to 10 bar.
  • filling is carried out to 5 bar in accordance with the control stand filling with a room volume of 2 dm3.
  • the pressure expansion chamber 15 of the cylinder IV has a room size of 3 dm3 which is filled with 3.75 bar of pneumatic volume.
  • the pressure expansion space of cylinder V is brought to 6.25 bar with 2 dm3 at 5 bar and the pressure expansion space 15 of cylinder VI with 1.75 dm3.
  • the pressure expansion chamber 15 of cylinder VII holds 1.20 dm3 at 8 bar and the pressure expansion chamber of cylinder VIII at 1 dm3 again has a pressure volume of 10 bar.
  • the pressure bypass chambers 16 of cylinders I and II are each filled with 1.6 dm3 and 12.5 bar. The same is in the pressure bypass chamber 16 of the cylinder III; the pressure bypass area of cylinder IV is in the retracted position and has no pressure or pressure volume.
  • the pressure bypass area of cylinder V is filled with 0.8 dm3 and 6.25 bar.
  • the pressure bypass chamber 16 of cylinder VI has a pressure of 7.8 bar with a room volume of 1.1 dm3.
  • the pressure bypass chamber 16 has a volume of 1.44 dm3 at 10 bar and cylinder VIII in the pressure bypass chamber 16 has a pressure chamber size of 1.6 dm3 at 12.5 bar.
  • control line there is an opened control pressure for controlling the control cylinder 8 of 12.5 bar.
  • the control line which was not drawn in for reasons of space, is operated in the control system approximately as the pressure bypass line shown in the system.
  • FIG. 2 shows this cylinder I with the pneumatic clamping pressure in the pressure expansion chamber 15 before the working thrust.
  • the sliding piston plate 2 is locked by means of the lock 3 'on the wall of the pressure cylinder.
  • Fig. 2 of the drawing shows the cylinder II with opened pneumatic clamping pressure with the sliding piston plate 11 retracted downwards together with the thrust supports 7 rigidly connected to them, so that these thrust supports 7 within the subsequent relief process in the pressure expansion chamber 15 the pneumatic pressure relief process by being placed on the Can not affect sliding piston plate 2 (before the working push).
  • the space between the sliding piston plate 2 and the sliding piston plate 9A is connected to the atmosphere via the connector 17.
  • the relay-controlled valves c embedded in the sliding piston plate 11 are open. The sliding piston plate 11 is moved within the pressure bypass chamber 16 without energy by the value of the spatial tension of the pressure expansion chamber 15 in relation to the relaxation path length.
  • Fig. 2 of the drawing shows the cylinder III in the position of the sliding piston plate 2 at the end of the working thrust, the locking 3 'released and the working sliding piston plate 2 down into the space cleared by the thrust supports 7 first by the path length down is moved until it rests on the thrust supports 7. It now inserts the pressure transfer from the pressure bypass chamber 16 into the subsequent containers or into the following cylinders. This is done via the constant energy pressure bypass line 28 (see the table).
  • Fig. 2 of the drawing shows the cylinder IV, in the position of the sliding piston at the end of the relief process.
  • the valves C are open during the lowering process of the sliding piston plate 11.
  • the pressure from the pressure bypass chamber 16 is passed into the following containers or into the following cylinders.
  • the remaining pneumatic pressure in the pressure bypass chamber 16 between the sliding piston plate 9 and the sliding piston plate 11 either remains in this space during the entire working process of the entire system connected in series during the bypassing process and is transferred into this space or, due to its small pressure size, it is by means of run over by a compressor 30 'drivable control cylinder 8 in the subsequent container or cylinder.
  • Cylinder V shows the position of the sliding piston plate in which the pressure fluid is completely transferred to the successive container or cylinder and a renewed loading of the pressure bypass chamber with pressure fluid can begin.
  • Cylinder V of FIG. 2 of the drawing shows the thrust piston rod 5, which is idle again via the crankshaft and connecting rods, the pressure-relieved pressure bypass chamber 16, the adjoining sliding piston plates 9 and 11 in the pressure bypass chamber 16, and the expanded pressure expansion chamber 15.
  • the thrust supports 7 of the sliding piston plate 11 lie on the underside of the sliding piston plate 2 and it can after the pressure expansion of the subsequent container, ie after its work and its beginning relief in this container or cylinder via the constant pressure bypass line 28 in the pressure bypass chamber 16 again injected pneumatic pressure (see table of the constant pressure circulation).
  • Fig. 2 of the drawing shows the cylinder VI shortly before the renewed work thrust.
  • the sliding piston plate 2 acting as a working piston is pressed up to the upper locking device 3 'by means of running over pressure fluid to the locking device 3' and the sliding piston plate 2 is locked at the top dead center.
  • the locking also takes place on the piston rod 5 by means of the locking 3 on the sliding piston plate 2.
  • cylinders VII and VIII are not shown in Fig. 2 of the drawing in order not to unnecessarily complicate the drawing. All subsequent containers have the same volume and are exposed to the same pressure. This ensures uniform pneumatic pressure transfer and pressure build-up in each working pressure vessel or cylinder with regard to pressure force and pressure volume.
  • the pneumatic pressure relief process with pressure transfer by means of the constant energy pressure bypass line 28 into the following cylinders takes place by the relaxation of the pneumatic pressure in the pressure expansion space 15 and the associated steady relaxation of the pneumatic pressure in the pressure bypass space 16, with simultaneous pneumatic pressure transfer and the energy saving of 80%.
  • the residual pneumatic volume, which is transferred by means of compression, is very small in relation to its volume and pressure. The transfer uses very little energy. In terms of design, care should be taken that the pneumatic pressure in the pressure expansion chamber 15 before the average 50% relaxation for the purpose of relieving work is equal to the pneumatic pressure in the pressure bypass chamber 16.
  • the cylinder system can be connected in parallel several times in order to achieve better rotational movements of the crankshaft.
  • Fig. 3 of the drawing shows a complete working phase of the cylinder III, with pressure transfer after the working stroke.
  • the last three representations of the cylinder concern the cylinder III a in its first position, then the cylinder III b in its subsequent position and the cylinder III c in its final position, in which the residual pressure from the pressure bypass chamber 16 by means of the lowerable sliding piston plate 9B from the Pressure bypass chamber 16 of the same has been transferred via the energy pressure bypass line 28 into the other storing pressure bypass rooms.
  • the sliding piston plate 9 can remain locked until the pressure volume from the pressure bypass chamber 16 of the cylinder III, which is first transferred into the cylinder VII, then into the cylinders VI-V and into the cylinder IV, has a pressure, which is less than the expanding pressure in the expansion space 15.
  • the locking of the sliding piston plate 9 is released, so that the thrust of the expansion pressure still present in the pressure expansion chamber 15 can transfer the pressure in the pressure bypass chamber 16 within the transfer to equalize a residual volume of 400 dm3.
  • the remaining transfer takes place by extending the pistons 51 of the control cylinder 8 according to FIG. 3 of the drawing in the cylinder position according to cylinder III c.
  • the control pressure in the control cylinder 8 is 12.5 bar by means of a small compressor or hydraulic pump, depending on the type of application of the corresponding pressure medium, up to a pressure of max. 15 bar brought, the pressure bypass chamber 16 is emptied.
  • the cylinder II due to its pressure volume in connection with the mechanical position of its parts, can do work by the expansion pressure in the pressure expansion space 15 expanding from 10 bar to 5 bar over a path length of 10 cm. At this moment, work on the piston rod is released in the form of an average force that is 750 kp over a path length of 10 cm.
  • the cylinder III according to FIG. 2 relieves the drawing, which its pressure bypass chamber 16 in which the cylinders VII-VI-V and IV within the pressure bypass chambers 16 are raised in the pressure volume, corresponding to the pressure volume in the pressure bypass chamber 16 of the cylinder III percentage decreases.
  • the constantly constant driving values which are approximately constant, can be seen from FIG. 2 of the drawing.
  • the cylinder I has meanwhile completed the process just described, and can now do work by means of pressure expansion in the pressure expansion chamber 15, the cylinder II initiating the relief process of the pressure bypass chamber 16, starting with the transfer of pressure into the cylinder VI and this to 90% of the required pressure volume brings in the pressure bypass chamber 16, so that in turn a residual pressure of 10% of the 10% pressure volume of cylinder II and cylinder VI must be returned in the reversing process.
  • the pressure volume required for a working stroke is 1000 cm3 at a pressure of 12.5 bar in the pressure bypass chamber 16, taking into account the one-off, initial filling torque of the pneumatic motor, 80-90% of which are generated by self-circulation and approx. 20-10% by small compressor 32 must be returned.
  • This corresponds to a rise in pressure of 3.75 bar and approximately 980 cm3 volume to 12.5 bar at 320 cm3 volume, based on the expansion phase of the work performed within a working stroke approx. 40% energy expenditure for this process.
  • the active and operating variant of the pneumatic motor is shown without pneumatic internal pressure circulation within the pressure bypass chambers 16.
  • the sliding piston plate 9 can be divided horizontally into a sliding piston plate 9A and a sliding piston plate 9B.
  • a ratchet lock 18 (FIG. 6) is arranged on the sliding piston plate 9A, in which the cylinder housing 5o of the controllable control cylinder 8 is fastened in a vertically movable manner, the piston 51 of which is fixedly attached to the sliding piston plate 9B with its piston rod 52.
  • the thrust supports 7 are slidable and run through all sliding piston plates and through the piston plate base plate 12.
  • the stroke length of the commute is 4o cm. Due to this stroke length, the expansion space volume in the expansion pressure space 15 has a pressure volume of 14 dm3 at 8o bar.
  • the plate of the sliding piston plate 9 is loaded with 122 bar on an area of 80 cm 2. This corresponds to the initial loading of the sliding piston plate 2 on the part of the expansion pressure space 15. However, this also guarantees that the sliding piston plate 2 is returned to the original tension value in order to obtain a new work performance.
  • a pneumatic or hydropneumatic pressure of 225-235 bar is used to prevent pressure relief within the pressure circulating spaces 16 during the pressure circulating process.
  • the control cylinders 8 have a cross-sectional size of 20 cm2 per stamp on their printing plate surfaces.
  • control cylinders 8 Two of these control cylinders 8 are stored in each working cylinder, so that a control pressure of approx. 9 t is applied to the pressure volume within the pressure bypassing spaces 16 during the pressure bypassing process at a 4o cm 2 high-pressure surface load.
  • the high-pressure control line is also switched via a flow compressor and pressure vessel. With the piston 51 of the control cylinder 8, it guarantees the presence of a constant high pressure during a change of control of the control cylinder, this pressure being increased by a few bar in order to be able to bypass the pressure volume in the working cylinder within the pressure bypass chamber 16.
  • control line which is connected to the control cylinder 8 is not shown for reasons of clarity.
  • the work involved over a 40 cm path length is 9 t. 4 of the drawing, 2 dm3 pressure volume at a pressure of 122 bar is injected into cylinders I and II and IV, III.
  • the stamps of the control cylinder 8 are due to the control position in the cylinder I and II in the retracted position, in the cylinder III and IV in the extended position.
  • the sliding piston plate 9 is slidably movable up to its uppermost locking position when the pressure and its volume are bypassed from the pressure bypass chamber 16 to the pressure bypass chamber 16.
  • the result of this is that the stamps of the control cylinders 8 move freely in the vertical direction when the pressure position is extended in the opening moment of the pressure opening spaces 16, as can be seen in the cylinder IV.
  • the control high pressure is switched to the control cylinder 8
  • the sliding piston plate 9A remains freely movable, the sliding piston plate 9B is locked and the sliding piston plate 9A moves vertically downwards to the sliding piston plate 9B, with the sliding piston plate 11 simultaneously the thrust supports 7 moves vertically downwards.
  • the vertical downward movement of these parts is 40 cm path length to ensure a working stroke.
  • the high-pressure stamp 8 moves by this difference, so that the expanding pressure means once on the cylinder housing 50 of the control cylinder 8 the surface of the sliding piston plate 2 generates a pressure effect from the pressure expansion space 15 and, on the other hand, the extending piston rods 52 of the control cylinder 8 are exposed to an equivalent counter-pressure effect by means of the surface of the sliding piston plate 9B if the pressure volume from the pressure bypass chamber 16 of the cylinder II is now in the by means of the small compressor 32 Pressure evacuation space 16 of the cylinder III is transferred.
  • the pressure expansion chamber 15 of the cylinder III compresses its expansion pressure volume from 14 dm 3 and 80 bar to 10 dm3 and 100 bar in this time sequence when the tension value is restored to achieve renewed work, the mechanical locks locking the sliding point when these sizes are reached.
  • the line 20 from the compressor 30 'to the room b of the control cylinder 8 was switched over in the cylinder IV and the control cylinder 8 retracted, the sliding piston plate 9A, as already explained, moving vertically downwards and laying on the locked sliding piston plate 9B .
  • the cylinder housing 50 of the control cylinder 8 are thus also moved vertically downwards.
  • the thrust supports 7 are also retracted mechanically when the valve "c" of the sliding piston plate 11 is open.
  • the expansion stroke of the cylinder IV begins, that is to say that work is carried out in the cylinder IV in that the sliding piston plate 2 is released from its locking.
  • the workflow just described completely within all cylinders is now shifted to the left by one cylinder in the following work phase according to FIG. 4 of the drawing.
  • the current pressure expansion phase within one cylinder is faster within the phase than the pressure circulation within the other cylinders. This is due to the corresponding cross-sectional sizes of the pressure bypass line 28 and the correspondingly lower printing speeds in relation to the expansion force.
  • the cross-section of all line systems should therefore be kept as large as possible and the row of cylinders of an engine block according to FIG. 4 of the drawing should be connected in parallel several times, it being possible to offset the individual pressure expansion stages in order to ensure a continuous crankshaft drive.
  • the pressure volume required for a working stroke is dm3 or 4000 cm3, taking into account the one-off filling torque within the pneumatic motor, at a pressure of 122 bar and with an energy expenditure of approx. 10 bar max. be bypassed once.
  • the energy expenditure for this working stroke within the control cylinder 8 is approximately equivalent to that just described.
  • the efficiency factor of the pneumatic motor increases by at least 700 to 800% in contrast to the conventional type of compression energy systems for operating pneumatic motors.
  • a pneumatic motor of this type needs around 20% of the work it produces to compare the operation of the system without taking wear and friction losses into account, in order to maintain the operator process and can continuously state 80% of the work as power for operating system systems.
  • the pneumatic pressure energy of 33 to approximately 60 or 70% stored in the pressure bypass chamber 16 of the pressure cylinder 1 before the working stroke of the sliding piston plate 2 is to be introduced into the pressure circulation line 28 without any expenditure of energy with gradual pneumatic pressure compensation.
  • the remaining percentages of pneumatic energy remaining in the pressure flow process must also be transferred by volume flow compressors in the same way.
  • the process just described can also take place via two separate pressure circulation lines 28, a pressure circulation line transferring potential energy in volume flow from cylinder to cylinder in the flow process and the transfer being carried out in series parallel to this process by means of a flow compressor.
  • a pressure circulation line transferring potential energy in volume flow from cylinder to cylinder in the flow process and the transfer being carried out in series parallel to this process by means of a flow compressor.
  • Another possibility of pneumatic pressure transfer for the entire potential energy to be transferred by means of a pressure circulation line 28 is possible with a flow compressor 32 within the pneumatic system in that the individual compression chambers of the overflow compressor, regardless of whether they are piston compressors or wheel compressors, have connecting pieces in which non-return valves are installed.
  • the constantly changing suction pressure from the pressure bypass chamber 16, from which the compressible medium is extended is to act on the reverse side on the surfaces of the parts in the bypass compressor which contribute to the compression. This saves enormous compressor performance and the potential energy of the free circulation transfer via the compressor or through the compressor does not impair the necessary transfer performance of the flow compressor or the flow compressors.
  • the flow compressor is intended to transfer some of the stored potential energy, for example from cylinder I to cylinders III-VIII, for further use.
  • Active power of a compressor with buffer volume within a pneumatic motor The compressed air has to suck out from the pressure bypass chamber 16 of the cylinder 1 in a very short time, for example similar to the expansion time of the air.
  • the potential energy has to be conveyed into the cylinders III-VIII via the pressure circulation line 28 in which a bypass is arranged in relation to the stroke volume of the compressor and a buffer volume container which is at least 10 times the stroke volume.
  • the pumping out of the air volume from cylinder I and the inflow of compressed air of, for example, up to 11 bar while observing the constructively promoted parameters for flow compressors into cylinders III-VIII are timed by control elements.
  • With a 10-fold cylinder stroke volume of the buffer the pressure only fluctuates by approx. 1 bar during the work cycles. Pressure can flow from the buffer into the cylinder volume of the leading piston in cylinder 3 even before it is fed from cylinder 1.
  • the isothermal coupling efficiency which is 0.534 kT from 1 bar to the respective nominal output, also improves by 60 when an overflow compressor works within a pneumatic motor due to the shortened operating time of the compressor, the pressure medium that is used, which loads the compressor with a medium pressure %. It increases from 0.534 kT to 0.854 kT.
  • the pneumatic motor in which work is carried out in the pressure evacuation chamber 15 of the individual cylinders by means of the sliding piston plate 2 in the relief process, should, in terms of effectiveness, perform the work which was carried out in the pressure circumvention rooms 16 of the individual cylinders.
  • the sliding piston plates 9a and 9b divide with the help of the extending control cylinders 8 and the residual pressure volume is transferred to the subsequent cylinder responsible for this at a constant pressure.
  • the parameters of increased pressure transfer do not have a disadvantageous effect in relation to the parameters of the always increasing mean pressure transfer in connection with the free pressure circulation, which are responsible for the performance of the flow compressor.
  • the circulation compressor now works with a work saving of 60% due to the existing pressure medium, i.e. to get 1100 Nm work per stroke of the system the circulation compressor requires an energy expenditure of 430 Nm at one changed clutch factor of 0.854. Because the overflow compressor only has to transfer a maximum of 50% of the pressure fluid, which overflows the other pressure fluid in its own pressure circulation, until the respective pressure equalization within the transfer cylinder, this output is divided again by two; taking into account friction and wear losses, it is possible to obtain a workload of up to 200% within the operating process of the system for a 100% energy expenditure.
  • an internal combustion engine which serves as the drive unit of the engine, is connected upstream of the pneumatic one, the effective factor performance of this engine can improve up to 100%.
  • a generator which is driven by means of the pneumatic motor can be connected to an electric motor with a downstream pneumatic motor for obtaining work. This guarantees that the electrical system operates within the operator process without energy expenditure and that up to 60% of the operator's own power required can be obtained either in the form of electrical energy from the generator or in the form of kinetic energy via the pneumatic motor.
  • each pressure bypass chamber 16 of a cylinder within the pneumatic motor is followed by a hydraulic tank in which the expanding pressure fluid can expand from the pressure bypass chamber 16 and thus shift the respective nominal pressure to the hydraulic oil.
  • the hydraulic oil circulated by means of the hydraulic pump and entering the tank again compresses the respective pressure fluid around the corresponding pressure bypass chambers. It should be noted that this variant never runs down to 1 bar in the pressure lowering and transfer process in the pressure lowering pressure bypass chamber 16.
  • a pressure fluid of medium pressure level must be run over by means of the control cylinders 8 and division of the sliding piston plates 9a and 9b from pressure bypass chamber 16 to pressure bypass chamber 16.
  • the performance of the hydraulic pump also relates to the average load in the bypass process.
  • a cooling system provided, which can be controlled by a temperature sensor, is switched on.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Claims (10)

  1. Procédé d'actionnement d'un moteur pneumatique avec utilisation d'un système d'actionnement qui comprend une pluralité de cylindres travaillants connectés en série, dont chacun présente une chambre de détente de pression fermée (15) qui renferme, pendant tout le temps de travail, une quantité d'air comprimé constante, dont la pression de contrainte développée avant la course de travail repousse le plateau de piston coulissant (2), après la course de travail, en se détendant en fonction de sa valeur de pression de contrainte intialement rélevée, sur la longueur de course de la détente nécessaire, avec production de travail, et, dans chaque cylindre travaillant, est agencée une chambre de transfert de pression (16) qui, d'une part, est reliée, à une conduite de pression et d'injection (27) raccordée à une source d'air comprimé (29) et reliée, à travers des soupapes relais commandées, à la chambre (16) de transfert de pression de tous les autres cylindres de pression travaillants et qui, d'autre part, est reliée à une conduite de transfert de pression (28) qui relie entre elles les chambres de transfert de pression (16) de tous les cylindres de pression travaillants, à travers des soupapes relais commandées, de sorte que le fluide travaillant qui se détend en sortant de la chambre de transfert de pression (16) est accumulé, en passant par la conduite de transfert de pression (28) pouvant être commandée par des soupapes relais, dans les chambres de transfert de pression (16) des cylindres de pression travaillants suivants et, pour relever la pression de contrainte pneumatique dans la chambre de détente de pression (15), en partie le fluide de pression réaccumulé dans les chambres de transfert de pression (16) de tous les cylindres travaillants suivants, est introduit par la conduite de transfert de pression d'énergie (28) commandée par relais, dans la chambre de transfert de pression (16), en partie dans une circulation de pression sans énergie, en partie au moyen d'un compresseur de recirculation (32), le fluide de pression qui est encore nécessaire pour développer la pression de contrainte nécessaire étant acheminé, par la conduite de pression et d'injection (27), en provenance d'une source (29) d'air comprimé alimentée en pression au moyen d'un compresseur (30), dans un processus d'actionnement continu de cylindre travaillant à cylindres travaillants, de sorte que le plateau de piston coulissant (2) qui joue le rôle de piston travaillant est repoussé vers le haut et que la pression de contrainte nécessaire pour la course de travail suivante est relevée dans la chambre de détente de pression (15).
  2. Procédé selon la revendication 1, caractérisé en ce que, dans le cas où l'on utilise, par exemple, huit cylindres travaillants (I-VIII), dans les chambres de transfert de pression (16) des trois premiers cylindres travaillants (I-III), 100 % de la pression de contrainte nécessaire sont introduits à partir de la source d'air comprimé (29), le troisième cylindre travaillant (III) exécutant la course de travail, la chambre de transfert de pression (16) du quatrième cylindre de travail (IV) étant tout d'abord reliée à la chambre de transfert de pression (16) du cylindre de pression travaillant (V) suivant, par la conduite de transfert de pression (28), sous la commande de relais, 50 % de la pression de contrainte étant accumulés dans cette chambre après l'équilibrage des pressions, après quoi la conduite de transfert de pression (28) est reliée au cylindre travaillant suivant où, de nouveau, à l'équilibrage des pressions, 50 % de cette pression de contrainte y sont accumulés et, aussitôt, et jusque pendant la marche, environ 80 % du fluide de pression sont accumulés et réutilisables.
  3. Procédé selon la revendication 1 ou 2, caractérisé en ce que le volume de pression qui reste en résidu dans la chambre de transfert de pression (16) après l'équilibrage des pressions est transféré dans les récipients suivants au moyen d'un compresseur de recirculation (30′) qui alimente un cylindre de commande (8).
  4. Procédé selon la revendication 1 ou 2, caractérisé en ce que la pluralité de cylindres travaillants connectés en série est utilisée plusieurs fois en parallèle pour garantir la continuité de l'entraînement du vilebrequin.
  5. Dispositif pour la mise en oeuvre du procédé selon les revendications 1 à 4, pour l'actionnement d'un moteur pneumatique avec utilisation d'un système d'actionnement, qui comprend une pluralité de cylindres travaillants connectés en série, dont chacun présente une chambre de détente de pression fermée (15) qui renferme, pendant tout le temps de travail, une quantité d'air comprimé constante, dont la pression de contrainte développée avant la course de travail repousse le plateau de piston coulissant (2), après la course de travail, en se détendant en fonction de sa valeur de pression de contrainte initialement relevée, sur la longueur de course de la détente nécessaire avec Production de travail et, dans chaque cylindre travaillant, est agencée une chambre de transfert de pression (16) qui, d'une part, est reliée à une conduite de pression et d'injection (27) raccordée à une source d'air comprimé (29) et reliée, à travers de soupapes relais commandées, à la chambre de transfert de pression (16) de tous les autres cylindres de pression travaillants et qui, d'autre part, est reliée à une conduite de transfert de pression (28) qui relie entre elles les chambres de transfert de pression (16) de tous les cylindres de pression travaillants, à travers des soupapes relais commandées, cependant que
       des compresseurs de transfert (32) sont agencés dans la conduite de transfert de pression (28),
       une source d'air comprimé (29) reliée à la conduite de pression et d'injection (27) est reliée à un compresseur (30) par lequel elle peut être alimentée en pression, et
       dans chaque cylindre, sont disposés des petits compresseurs (30′), agissant sur des cylindres de commande (8) et qui servent à vider totalement la chambre de transfert de pression (16)
       et chaque cylindre travaillant (1) comprend, comme piston travaillant, un plateau de piston coulissant (2) qui est adjacent à la chambre de détente de pression (14), qui peut être verrouillé, au moyen d'un verrouillage (3) appartenant à une serrure de verrouillage (6), par rapport à la tige de piston (5) enfilée dans un guide (4), et à une certaine distance au-dessous du plateau de piston coulissant (2) est agencé un plateau de piston coulissant (9) qui limite la chambre de transfert de pression (16) et au-dessous de ce dernier, est agencé un plateau de piston coulissant (11) muni de soupapes commandées (c), la chambre de transfert de pression (16) étant fermée vers le bas par une plaque de fond de plateau de piston (12) qui peut être verrouillée.
  6. Dispositif selon la revendication 5, caractérisé en ce que le guide (4) de tige de piston (5) qui est relié rigidement au plateau de piston coulissant (2) peut être verrouillé ou déverrouillé par rapport au corps du cylindre (1) au moyen d'un verrouillage (3′).
  7. Dispositif selon une des revendications 5 et 6, caractérisé en ce que, dans la paroi de chaque cylindre (1), sont prévues une tubulure d'amenée de pression (13) qui débouche dans la chambre de détente de pression (15) et une tubulure d'amenée de la pression (14) qui débouche dans la chambre de transfert de pression (16) de ce cylindre, qui sont toutes deux reliées à une conduite de pression et d'injection (27) qui est en liaison avec la source d'air comprimé (29) et, dans la paroi latérale de chaque cylindre (1), est agencée une tubulure de liaison (17) qui relie à l'atmosphère la chambre située entre le plateau de piston coulissant (2) et le plateau de piston coulissant supérieur (9A), cette tubulure étant agencée dans la région inférieure de cette chambre.
  8. Dispositif selon une des revendications 5 à 7, caractérisé en ce qu'il est prévu une conduite de transfert de pression (28) munie de soupapes relais commandées, qui relie entre elles les chambres de transfert de pression (16) de tous les cylindres travaillants, et par l'intermédiaire de laquelle le fluide travaillant qui se détend en sortant de la chambre de transfert de pression (16) est accumulé dans les chambres de transfert de pression (16) des cylindres travaillants suivants, et, en outre, lors de la remontée de la pression de contrainte pneumatique, le fluide de pression accumulé est introduit dans la chambre de transfert de pression (16), en partie par circulation de pression sans énergie et en partie à l'aide de compresseurs de recirculation (32).
  9. Dispositif selon une des revendications 5 à 8, caractérisé en ce que le plateau de pistons coulissants (9) est subdivisé en deux plateaux de piston coulissant (9A et 9B) et le plateau de piston coulissant supérieur (9A) est relié au corps de cylindre (50) du cylindre de commande (8) qui peut être alimenté en fluide de pression à partir d'un accumulateur de pression, tandis que le plateau de piston coulissant inférieur (9B) est relié à la tige de piston (52) d'un piston (51) de ce cylindre de commande (8), qui peut être alimenté sur les deux faces et peut se déplacer en mouvement ascendant et descendant.
  10. Dispositif selon une des revendications 5 à 9 précédentes, caractérisé en ce que le plateau de piston coulissant (11) est relié rigidement à des supports de poussée (7) s'étendant vers le haut et vers le bas, dont les parties qui s'étendent vers-le haut traversent les plateaux de pistons coulissants (9A et 9B) en y coulissant à joint étanche, et dont les parties qui s'étendent vers le bas traversant la plaque de fond de plateau coulissant (12), en y coulissant à joint étanche.
EP91107221A 1990-05-04 1991-05-03 Procédé d'opération d'un moteur pneumatique et dispositif pour l'exécution de ce procédé Expired - Lifetime EP0455258B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT91107221T ATE87351T1 (de) 1990-05-04 1991-05-03 Verfahren zum antrieb eines pneumatischen motors und vorrichtung zur durchfuehrung des verfahrens.

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE4014372 1990-05-04
DE4014372 1990-05-04
DE19904031324 DE4031324A1 (de) 1990-10-04 1990-10-04 Verfahren zum antrieb eines pneumatischen motors und vorrichtung zur durchfuehrung des verfahrens
DE4031324 1990-10-04

Publications (2)

Publication Number Publication Date
EP0455258A1 EP0455258A1 (fr) 1991-11-06
EP0455258B1 true EP0455258B1 (fr) 1993-03-24

Family

ID=25892862

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91107221A Expired - Lifetime EP0455258B1 (fr) 1990-05-04 1991-05-03 Procédé d'opération d'un moteur pneumatique et dispositif pour l'exécution de ce procédé

Country Status (9)

Country Link
US (1) US5375417A (fr)
EP (1) EP0455258B1 (fr)
JP (1) JPH05506903A (fr)
AU (1) AU7774891A (fr)
BR (1) BR9106416A (fr)
CA (1) CA2075630A1 (fr)
DE (1) DE59100064D1 (fr)
ES (1) ES2040606T3 (fr)
WO (1) WO1991017344A1 (fr)

Families Citing this family (35)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5515675A (en) * 1994-11-23 1996-05-14 Bindschatel; Lyle D. Apparatus to convert a four-stroke internal combustion engine to a two-stroke pneumatically powered engine
DE59602539D1 (de) * 1995-05-16 1999-09-02 Truninger Ag Vorrichtung zum kontrollierten antrieb wenigstens einer hydraulischen achse
US5806314A (en) * 1995-10-03 1998-09-15 Joseph F. Younes Pressurized cylinder and booster in a low volume pressure circuit
KR19990062360A (ko) * 1997-12-31 1999-07-26 하석봉 공기압을 이용한 실린더 상하 구동장치
US6626079B1 (en) * 2002-03-28 2003-09-30 Rehco, Llc Pneumatic motor
FR2880649A1 (fr) * 2005-01-07 2006-07-14 Raymond Louis Espitalie Dispositif hybride electro-pneumatique, generateur d'une energie motrice non polluante a deux temps
KR100999017B1 (ko) 2008-02-14 2010-12-09 강형석 압축공기를 이용한 실린더를 갖는 엔진
US8448433B2 (en) 2008-04-09 2013-05-28 Sustainx, Inc. Systems and methods for energy storage and recovery using gas expansion and compression
US8479505B2 (en) 2008-04-09 2013-07-09 Sustainx, Inc. Systems and methods for reducing dead volume in compressed-gas energy storage systems
US7958731B2 (en) 2009-01-20 2011-06-14 Sustainx, Inc. Systems and methods for combined thermal and compressed gas energy conversion systems
US8474255B2 (en) 2008-04-09 2013-07-02 Sustainx, Inc. Forming liquid sprays in compressed-gas energy storage systems for effective heat exchange
US8225606B2 (en) 2008-04-09 2012-07-24 Sustainx, Inc. Systems and methods for energy storage and recovery using rapid isothermal gas expansion and compression
US8359856B2 (en) 2008-04-09 2013-01-29 Sustainx Inc. Systems and methods for efficient pumping of high-pressure fluids for energy storage and recovery
US8240140B2 (en) 2008-04-09 2012-08-14 Sustainx, Inc. High-efficiency energy-conversion based on fluid expansion and compression
US7802426B2 (en) 2008-06-09 2010-09-28 Sustainx, Inc. System and method for rapid isothermal gas expansion and compression for energy storage
WO2009126784A2 (fr) 2008-04-09 2009-10-15 Sustainx, Inc. Systèmes et procédés de stockage et de récupération d’énergie à l’aide de gaz comprimé
US20100307156A1 (en) 2009-06-04 2010-12-09 Bollinger Benjamin R Systems and Methods for Improving Drivetrain Efficiency for Compressed Gas Energy Storage and Recovery Systems
US8037678B2 (en) 2009-09-11 2011-10-18 Sustainx, Inc. Energy storage and generation systems and methods using coupled cylinder assemblies
US8250863B2 (en) 2008-04-09 2012-08-28 Sustainx, Inc. Heat exchange with compressed gas in energy-storage systems
US8677744B2 (en) 2008-04-09 2014-03-25 SustaioX, Inc. Fluid circulation in energy storage and recovery systems
WO2010105155A2 (fr) 2009-03-12 2010-09-16 Sustainx, Inc. Systèmes et procédés destinés à améliorer le rendement de transmission pour le stockage d'énergie sous forme de gaz comprimé
US8104274B2 (en) 2009-06-04 2012-01-31 Sustainx, Inc. Increased power in compressed-gas energy storage and recovery
WO2011056855A1 (fr) 2009-11-03 2011-05-12 Sustainx, Inc. Systèmes et procédés de stockage d'énergie produite par un gaz comprimé au moyen d'ensembles vérins couplés
US8191362B2 (en) 2010-04-08 2012-06-05 Sustainx, Inc. Systems and methods for reducing dead volume in compressed-gas energy storage systems
US8171728B2 (en) 2010-04-08 2012-05-08 Sustainx, Inc. High-efficiency liquid heat exchange in compressed-gas energy storage systems
US8234863B2 (en) 2010-05-14 2012-08-07 Sustainx, Inc. Forming liquid sprays in compressed-gas energy storage systems for effective heat exchange
US8495872B2 (en) 2010-08-20 2013-07-30 Sustainx, Inc. Energy storage and recovery utilizing low-pressure thermal conditioning for heat exchange with high-pressure gas
US8578708B2 (en) 2010-11-30 2013-11-12 Sustainx, Inc. Fluid-flow control in energy storage and recovery systems
EP2715075A2 (fr) 2011-05-17 2014-04-09 Sustainx, Inc. Systèmes et procédés pour un transfert thermique biphasé efficace dans des systèmes de stockage d'énergie à air comprimé
US20130091836A1 (en) 2011-10-14 2013-04-18 Sustainx, Inc. Dead-volume management in compressed-gas energy storage and recovery systems
CN103075196A (zh) * 2013-01-05 2013-05-01 刘典军 压缩空气循环做功的气动马达
CN103089313B (zh) * 2013-01-28 2015-02-18 冯袖幅 一种气能机
US10641094B2 (en) 2015-04-10 2020-05-05 The Centripetal Energy Company Ii Pressure differential engine
CN106112439B (zh) * 2016-08-15 2018-07-31 大连华控工业装备有限公司 双列圆锥轴承自动定心密封罩压合机
EP3652417B1 (fr) * 2017-07-10 2022-12-28 Burckhardt Compression AG Procédé et dispositif pour détendre un gaz au moyen d'un moteur à piston

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US626368A (en) * 1899-06-06 Vertical engine
US380375A (en) * 1888-04-03 willans
DE565927C (de) * 1929-09-11 1932-12-12 Olav Eskil Jorgensen Druckluftspeicher zum Betrieb von Druckluftmotoren
GB1007383A (en) * 1962-09-28 1965-10-13 John Ragnar Johansson Improvements in hydraulic or pneumatic reciprocating motors
US3152517A (en) * 1963-02-15 1964-10-13 Air Prod & Chem Reciprocating piston engine
US3367238A (en) * 1964-04-23 1968-02-06 Int Nickel Co Valve and method for operating mechanical tuyere puncher and the like
US3925984A (en) * 1973-12-05 1975-12-16 John E Holleyman Compressed air power plant
US4354421A (en) * 1980-07-18 1982-10-19 Exxon Research & Engineering Co. Energy recovery reciprocating engine
DK149514C (da) * 1983-09-16 1986-12-22 Danfoss As Hydraulisk aktuator til styring af ventiler

Also Published As

Publication number Publication date
BR9106416A (pt) 1993-05-04
AU7774891A (en) 1991-11-27
US5375417A (en) 1994-12-27
DE59100064D1 (de) 1993-04-29
WO1991017344A1 (fr) 1991-11-14
CA2075630A1 (fr) 1991-11-05
JPH05506903A (ja) 1993-10-07
ES2040606T3 (es) 1993-10-16
EP0455258A1 (fr) 1991-11-06

Similar Documents

Publication Publication Date Title
EP0455258B1 (fr) Procédé d'opération d'un moteur pneumatique et dispositif pour l'exécution de ce procédé
WO2002024441A1 (fr) Dispositif de commande pour une presse hydraulique et procede pour son fonctionnement
DE3640788A1 (de) Zieheinrichtung fuer eine presse
DE2633233A1 (de) Waermekraftmashine mit aeusserer waermequelle
DE2845058A1 (de) Freikolbenmotorpumpe mit energieabgabeglaettung
EP0972631B1 (fr) Entraínement hydraulique pour une presse
EP3620296B1 (fr) Presse à balles ainsi que procédé de commande pour une telle presse à balles
DE102012104125A1 (de) Verfahren zum Betreiben einer hydraulischen Presse und eine hydraulische Presse
DE3780595T2 (de) Hydraulisch-pneumatische leistungsuebertragungseinrichtung.
EP2420681A2 (fr) Entraînement linéaire hydraulique
DE4210504A1 (de) Antrieb zur Hubverlagerung für Umformmaschinen
DE1907077A1 (de) Presse und Verfahren zum Tiefziehen von Blechrohlingen zu Behaeltern
DE2349351C3 (de) Hydrauliksystem für eine Presse
DE4320213A1 (de) Stauchpressenhauptantrieb
DE4218952B4 (de) Hydraulischer Antrieb für eine Presse, insbesondere für eine Blechformpresse
DE102013007148A1 (de) Hydraulischer Pressantrieb mit Energierückspeisung
DE102013014074B3 (de) Ballenpresse
DE102019002370A1 (de) Hydraulische Kolbeneinrichtung, welche mindestens zum Zwecke einer Gasverdichtung verwendbar ist, Druckgasenergiewandlungseinrichtung, Druckgasenenergiewandlungs-Wärmetauscher-Einrichtung, Druckgasenergiewandlungs-Wärmetauscher-Einrichtungs-Vorstufeneinrichtung und Druckgasenenergiewandlungsvorrichtung
DE102018203367A1 (de) Hydrostatischer Linearantrieb
DE2419715A1 (de) Thermohydraulischer motor
DE4101299A1 (de) Verfahren zum antrieb eines pneumatischen motors und vorrichtung zur durchfuehrung des verfahrens
DE102008056717A1 (de) Freikolben-Brennkraft-Hydro-Maschine
DE4031324A1 (de) Verfahren zum antrieb eines pneumatischen motors und vorrichtung zur durchfuehrung des verfahrens
EP0957250A2 (fr) Moteur à combustion interne
DE153570C (fr)

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH DE DK ES FR GB GR IT LI LU NL SE

17P Request for examination filed

Effective date: 19910925

17Q First examination report despatched

Effective date: 19920213

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH DE DK ES FR GB GR IT LI LU NL SE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 19930324

Ref country code: DK

Effective date: 19930324

REF Corresponds to:

Ref document number: 87351

Country of ref document: AT

Date of ref document: 19930415

Kind code of ref document: T

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19930421

Year of fee payment: 3

REF Corresponds to:

Ref document number: 59100064

Country of ref document: DE

Date of ref document: 19930429

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: LU

Payment date: 19930430

Year of fee payment: 3

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 19930505

Year of fee payment: 3

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19930507

Year of fee payment: 3

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 19930517

Year of fee payment: 3

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 19930520

Year of fee payment: 3

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19930423

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 19930531

Year of fee payment: 3

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: BE

Payment date: 19930614

Year of fee payment: 3

ITF It: translation for a ep patent filed

Owner name: UFFICIO BREVETTI RICCARDI & C.

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 19930719

Year of fee payment: 3

ET Fr: translation filed
EPTA Lu: last paid annual fee
REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2040606

Country of ref document: ES

Kind code of ref document: T3

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19940503

Ref country code: AT

Effective date: 19940503

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Effective date: 19940504

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19940504

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Effective date: 19940531

Ref country code: CH

Effective date: 19940531

Ref country code: BE

Effective date: 19940531

BERE Be: lapsed

Owner name: BARTH WOLFGANG

Effective date: 19940531

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Effective date: 19941201

NLV4 Nl: lapsed or anulled due to non-payment of the annual fee
EUG Se: european patent has lapsed

Ref document number: 91107221.3

Effective date: 19941210

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Effective date: 19950131

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Effective date: 19950201

EUG Se: european patent has lapsed

Ref document number: 91107221.3

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19950503

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19950503

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 19990503

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20050503