US3771421A - Thrust piston motors - Google Patents

Thrust piston motors Download PDF

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Publication number
US3771421A
US3771421A US00129756A US3771421DA US3771421A US 3771421 A US3771421 A US 3771421A US 00129756 A US00129756 A US 00129756A US 3771421D A US3771421D A US 3771421DA US 3771421 A US3771421 A US 3771421A
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United States
Prior art keywords
piston
control valve
valve
cylinder
main control
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Expired - Lifetime
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US00129756A
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English (en)
Inventor
H Scheffer
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Harry Krueger GmbH
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Harry Krueger GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L25/00—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means
    • F01L25/02—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by fluid means
    • F01L25/04—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by fluid means by working-fluid of machine or engine, e.g. free-piston machine
    • F01L25/06—Arrangements with main and auxiliary valves, at least one of them being fluid-driven
    • F01L25/063—Arrangements with main and auxiliary valves, at least one of them being fluid-driven the auxiliary valve being actuated by the working motor-piston or piston-rod
    • 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
    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04B15/02—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts the fluids being viscous or non-homogeneous
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/12—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/12—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air
    • F04B9/123—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having only one pumping chamber
    • F04B9/125—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having only one pumping chamber reciprocating movement of the pumping member being obtained by a double-acting elastic-fluid motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/12—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air
    • F04B9/129—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers
    • F04B9/137—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers the pumping members not being mechanically connected to each other
    • F04B9/1372—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers the pumping members not being mechanically connected to each other the movement of each pump piston in the two directions is obtained by a double-acting piston fluid motor

Definitions

  • ABSTRACT A control device for a thrust piston motor consisting of two normally closed auxiliary control valves and one main control valve, controlled by the auxiliary control valves, and containing a control piston adapted to be displaced by the action of the fluid medium and a control slide coupled with the control piston for controlling the direction of movement of the motor piston, and wherein the control pressure chambers are each connected by a bore provided in the control piston and a supplementary valve means connected to the control piston, with a pressure medium source and through one of the auxiliary control valves each with a low pressure zone the improvement comprising that for obtaining an externally controlled sequence of individual strokes, one control valve (first control valve) is operable externally and the other control valve (second control valve) by the motor piston during the passage through a dead centre position, wherein there is mounted, on the side of the motor piston remote from the second control valve in the motor cylinder, an abutment stop in such a manner that its distance from the second control valve is
  • the invention relates to a thrust piston motor operated with a gaseous fluid medium, comprising a control device consisting of two normally closed auxiliary control valves and one main control valve controlled by the auxiliary control valves, and containing a control piston adapted to be displaced by the action of the fluid medium and a control slide coupled with the control piston for controlling the direction of movement of the engine piston, and wherein the control pressure chambers are each connected by a bore provided in the control piston and a supplementary valve means connected to the control piston with the pressure medium source, and through one of the auxiliary control valves each with a low pressure zone.
  • Known thrust piston motors with linkage-less control of the type hereinbefore mentioned are unsuitable for driving working appliances which require an externally controlled sequence of individual strokes.
  • Such appliances e.g., charging pumps with or without. variable metering of the amount of the charge, which must be operated whenever the container to be filled is located underneath the outlet of the pump.
  • the invention has the object of providing a thrust piston motor of the kind hereinbefore mentioned and which is controllable externally to achieve a sequence of individual strokes. It is a further object of the invention to provide a thrust piston motor with variable piston stroke. Furthermore, this motor should operate perfectly under all operating conditions. Its operating behaviour should be substantially independent of the frequency of the stroke sequence.
  • control valve (the first control valve) is actuable externally and the other control valve (second control valve) is actuable by the motor piston when passing through a dead centre position.
  • the thrust piston motor is made to oscillate automatically by an externally applied pulse.
  • This continuous operation is necessary particularly for the operation of charging pumps, where these pumps are intended to induct a cleaning agent and to deliver the same so that the pump chamber of the pump may be cleaned when switching from one substance to be charged to another.
  • the abutment is connected to a third control valve which is normally closed and opens towards a zone with lower pressure, and a three-way valve is connected between the first control valve and the main control valve, whereby the third control valve may be connected to the main control valve while separating the first control valve from the main control valve.
  • FIG. 1 is a basic diagram of the invention, showing in partial cross-section the arrangement with the threeway cock in one position;
  • FIG. 2 shows another position of the three-way cock
  • FIG. 3 shows another embodiment of the thrust piston motor in accordance with the invention
  • FIG. 4 shows yet another embodiment of the thrust piston motor according to the invention
  • FIG. 5 shows the use of the thrust piston motor according to the invention as a metering device.
  • the thrust piston motor in accordance with the invention consists substantially of a cylinder 1, a piston 2, three control valves 3, 4 and 5, a main control valve 6 and a three-way cock 7.
  • the cylinder 1 consists of an upper cylinder cover la, a lower cylinder cover 1b and an annular cylinder body 10.
  • a sleeve-shaped abutment bush 9 with an external thread 10 is screwed into a bore 8 in the upper cylinder cover.
  • a locknut I1 screwed on to the external thread 10, is seated on the other surface of the cylinder cover la, thereby fixing the abutment bush 9 in its position in the cover.
  • the abutment bush 9 has a bore 12 with internal thread, into which the third control valve is screwed.
  • the third control valve 5 is actuable by the motor piston 2. Its construction will be described further below.
  • In the cylinder cover lla there is also a bore 13 which communicates through a conduit 14 with a port 15 in the valve block 6a of the main control valve 6.
  • the piston rod of the piston 2 passes through the cylinder cover lb.
  • the cylinder cover has a bore 16a, connected by a conduit 17 with a port 16 in the valve block 6a.
  • the second control valve 4 is screwed into a third bore 18 in the cylinder cover 1b, and communicates through a conduit 19 with a control pressure chamber 20 of the main control valve. Also the construction of the control valve 4, which is identical to the construction of the control valve 5, will be discussed further below.
  • the first control valve 3 is connected with the three-way cock through a conduit 35.
  • the control valve 3 is screwed into a carrier plate 36 which may form part of a roller track on a filler path.
  • the valve 3 is adapted to be operated by an actuating pin 3a.
  • the valve 3 may also be a pedal operated valve, in which an operator in the filling station contacts the pin 3a with his foot.
  • the three-way cock 7 may connect either the first control valve 3 with the control pressure chamber 26 or the third control valve 5 with this control pressure chamber.
  • the first position is shown in FIG. 1 and the second in FIG. 2.
  • FIG. 1 also indicates that the control valve 3 may be used for operating further thrust piston motors 37 and 38.
  • valves 3, 4 and 5 have the same construction. They open towards a lower pressure zone.
  • the construction will now be described with reference to the valve 3.
  • a connecting conduit 30 which connects the interior of the control valve housing 3b with a lower pressure zone.
  • a sealing body 3d is movably mounted in the control valve housing, and surrounds in one end position the end of the connecting conduit 30, located in the control valve housing, sealing by means of a seal 3e.
  • the actuating pin 3a protruding from the valve housing 31) rests via a compression spring 3fon the sealing body 3d in such a manner that during its forward movement, first the compression spring 3f is biased and then the sealing body 3d is lifted off its seat 3e.
  • the sealing body 3d is pressed onto its seat by means of a spring 3g.
  • the main control valve 6, 306, 406 has two operating positions. As known in the art, the valve applies during the response of the upper control valve 5, 305, 405, the operating pressure to the cylinder chamber above the piston l, 301, 401, while opening the chamber under the piston to low pressure. When the lower control valve 4, 304, 404 responds, it applies the operating pressure to the cylinder chamber under the piston 1, 301, 401 and opens the chamber above the piston to low pressure. When both control valves are connected with the main control valve, the piston continues to move up and down.
  • the piston carries out only a single stroke in both directions, when the external valve is actuated, and remains when stationary on the side of the disconnected control valve.
  • the three-way cock 7 is in the position shown in FIG. 1. In this way, the motor is prepared for single stroke sequence.
  • the piston 2 rests on the abutment bush 9.
  • the control pressure chamber 26 is vented through the conduit 34 so that the control piston 21 moves towards the top.
  • the control slide 28 connects the port 16a in the lower cylinder cover 1b through the conduit 17 with the pressure medium outlet 29. Since at the same time the working pressure chamber 22 is connected by the port 15 and the conduit 14 with the cylinder chamber above the piston, the piston 2 in FIG. 1 is pushed down.
  • control piston is then displaced very forcibly towards the bottom.
  • the sleeve is also accelerated so that it moves further towards the bottom, when the piston 21 has already reached its bottom dead centre piston. Since then the port 24a is opened, lower control chamber 20, reduced to its minimum volume, will again close through the bore 24 the control valve 4, which has been opened by the action of the compression spring 4fand the conduit 19 will become pressurized.
  • the three-way cock 7 is moved into the position shown in FIG. 2. This connects the upper control pressure chamber 26 with the third control valve 5.
  • the valve 5 is operated in the same manner as the valve 4. All three valves 3, 4, and 5 make possible a sudden, shock-like opening, giving rise to a sudden movement of the main control valve piston so that the motor piston 2 does not remain long in its end positions.
  • the locknut 11 is slackened, so that the abutment bush 9 can be rotated in the bore 8.
  • the transmission member 31 and the flexible transfer element 32 are necessary to enable the valve 5, firmly connected to the bush 9, to be raised, lowered and rotated relative to the conduit 33.
  • FIG. 3 shows another arrangement, the effects of 5 which are the same as described above.
  • the conduit 304 on the lower cylinder plate 3011b communicates in this construction with the conduit to the three-way cock 307.
  • This connects the control valve 304 with the main control valve 306 or with the externally operable valve 303.
  • the control valve 305 adapted to be adjusted by means of the abutment bush 309 is connected by a flexible conduit 332 directly with the other side of the main control valve 306.
  • this arrangement has the advantage that the piston remains stationary in its lower position when the three-way cock is switched to individual operation.
  • the adjustable control valve 305 may therefore be adjusted to the required stroke without interference by the piston.
  • the upper control valve 405 has exactly the same construction as the lower control valve 404 and is mounted in the same manner as the latter in the upper'cylinder plate 401a.
  • this upper cylinder plate 401a has mounted thereon, in front of the control valve 405, a plate 440, having along its periphery milled grooves 441 into which engage retaining angles 442, mounted on the cylinder cover 401a.
  • the plate 440 is therefore secured against rotation, but may carry out limited movements up and down within the range of the retaining angles, which are just sufficient for operating the control valve 405.
  • the centre of the plate 442 is provided with a threaded bore 443 adapted to receive a spindle 444.
  • This spindle is connected by means of a square section element 445 and a screw 446 with a cap 447 in such a manner that a rotation of the cap 447 will also entrain a rotation of the spindle 444.
  • a sleeve 448 is firmly screwed into the cylinder cover 401a and a seal prevents the loss of compressed air when the upper cylinder chamber is vented. By rotating the cap 447, the piston stroke can again be adjusted without interference by the piston.
  • the spindle 444 is fixed by a screw 450 engaging into the cap 447, relative to the sleeve 449 and therefore relative to the cylinder.
  • the piston In its top position, the piston abuts against the spindle 444 and lifts thereby the plate 442 until the same operates the control valve 405.
  • the piston carries out, as in the arrangement of FIG. 3, a reciprocating movement or a single stroke movement, returning thereafter into its bottom position and remaining there, according to the position of the three-way cock.
  • This construction has the advantage that the flexible conduit has been omitted which might lead to difficulties, while the adjusting capabilities of the piston stroke have been maintained.
  • FIG. 5 shows diagrammatically the operation of a charging installation equipped with thrust piston motors in accordance with the invention.
  • the tank 501 contains a polyester resin, the tank 502 a hardener therefor which is to be added to the first substance in a certain mixing ratio.
  • the vessel 501 is connected with a first metering pump 503, the piston of which is actuated by a thrust piston motor 504 in accordance with the invention.
  • the vessel 502 is connected with a second metering pump 505, the piston of which is actuated by a thrust piston motor 506. Both thrust piston motors may be operated at choice through a switching valve assembly 507 in individual operation or in reciprocating movement.
  • the normal filling operation is effected in that way that, upon actuation of the switching valve assembly 507, the pistons of both motors move up and induct through the suction valves 508 and 509 a metered amount of the substance to be charged. After reaching their topmost position, the pistons return and eject the metered amounts through ejection valves 510 and 511 into the mixing tank 512.
  • the vessels 501 and 502 are replaced by vessels with a solvent.
  • the thrust piston motors 505 and 506 are set at reciprocating operation and pump the solvent to the collection tank, thereby removing all resinous residues.
  • a thrust piston motor operated by a gaseous pressurized fluid comprising, in combination, a cylinder having first and second heads, a piston having opposite sides and reciprocally mounted within said cylinder having a piston rod extending through one of said heads, a main control valve connected to a source of pressurized gaseous fluid, a pair of flow conduits connecting said control valve to said cylinder and comm unicating with opposite sides of said piston, a valve spool movably mounted within said control valve selectively connecting said flow conduits with the source of pressurized gaseous fluid and the ambient atmosphere, first and second reversing valves mounted adjacent said first and second cylinder heads, respectively, each selectively communicating with said main control valve whereby actuation of one of said reversing valves shifts said valve spool to reverse the direction of movement of said piston within said cylinder, actuating means mounted upon each of said reversing valves sensing the position of said piston as it approaches the associated cylinder head, a remote control valve located remotely from said cylinder, first
  • abutment means mounted in said first head axially movable toward and away from said piston engagable by said piston to limit movement of said piston toward said first head, and means interconnecting said first reversing valve with said abutment means wherein said first reversing valve is operative to operate said main control valve and valve spool at all positions of said abutment means.
  • a thrust piston motor operated by a gaseous pressurized fluid comprising, in combination, a cylinder having first and second heads, a piston having opposite sides and reciprocally mounted within said cylinder having a piston rod extending through one of said heads, a main control valve connected to a source of pressurized gaseous fluid, a pair of flow conduits connecting said control valve to said cylinder and communicating with opposite sides of said piston, a valve spool movably mounted within said control valve selectively connecting said flow conduits with the source of pressurized gaseous fluid and the ambient atmosphere, first and second reversing valves mounted adjacent said first and second cylinder heads, respectively, each selectively communicating with said main control valve whereby actuation of one of said reversing valves shifts said valve spool to reverse the direction of movement of said piston within said cylinder, actuating means mounted upon each of said reversing valve sensing the position of said piston as it approaches the associated cylinder head, abutment means threadedly mounted on said first head axially adjustably

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Fluid-Driven Valves (AREA)
  • Multiple-Way Valves (AREA)
  • Processing And Handling Of Plastics And Other Materials For Molding In General (AREA)
US00129756A 1970-04-01 1971-03-31 Thrust piston motors Expired - Lifetime US3771421A (en)

Applications Claiming Priority (1)

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DE19702015472 DE2015472A1 (de) 1970-04-01 1970-04-01 Schubkolbenmotor

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US3771421A true US3771421A (en) 1973-11-13

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US00129756A Expired - Lifetime US3771421A (en) 1970-04-01 1971-03-31 Thrust piston motors
US00129861A Expired - Lifetime US3745886A (en) 1970-04-01 1971-03-31 Thrust piston motor operating with a gaseous fluid medium

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US (2) US3771421A (enrdf_load_stackoverflow)
DE (1) DE2015472A1 (enrdf_load_stackoverflow)
FR (2) FR2092512A5 (enrdf_load_stackoverflow)
GB (2) GB1303004A (enrdf_load_stackoverflow)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3943823A (en) * 1974-06-13 1976-03-16 Nordson Corporation Control system for double acting air motor
EP0045536A1 (en) * 1980-08-04 1982-02-10 Manfred Berweger A multi-component delivery apparatus
US4398463A (en) * 1981-08-19 1983-08-16 Motter Printing Press Co. Non-repeat doctor blade drive
US4738107A (en) * 1983-04-22 1988-04-19 Carlander Lars Erik Device in an actuator for elevation adjustment of work stations
US5454290A (en) * 1992-10-15 1995-10-03 Bendix Espana S.A. Hydraulic control device with movable valve
US6398527B1 (en) * 2000-08-21 2002-06-04 Westport Research Inc. Reciprocating motor with uni-directional fluid flow
US20090211434A1 (en) * 2008-02-26 2009-08-27 Lauder Arthur W Fluid pressure powered apparatus
US20230046193A1 (en) * 2019-09-19 2023-02-16 Oshkosh Corporation Reciprocating piston pump
US12404847B2 (en) * 2023-10-23 2025-09-02 Oshkosh Corporation Reciprocating piston pump

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GB2266579B (en) * 1992-04-16 1995-12-20 Baj Ltd Gas operated ejection system
US5927954A (en) * 1996-05-17 1999-07-27 Wilden Pump & Engineering Co. Amplified pressure air driven diaphragm pump and pressure relief value therefor
DE19860466C1 (de) * 1998-12-28 2000-06-29 Schmidt & Co Gmbh Kranz Pneumatisch angetriebene Hydraulikpumpe
RU2352797C2 (ru) * 2007-04-27 2009-04-20 Анатолий Александрович Рыбаков Способ привода клапана рабочим телом поршневой машины
RU2349765C1 (ru) * 2007-11-06 2009-03-20 Анатолий Александрович Рыбаков Пневматический привод клапана однотактного свободнопоршневого двигателя с внешней камерой сгорания
RU2426900C1 (ru) * 2010-03-12 2011-08-20 Анатолий Александрович Рыбаков Способ оптимизации процесса расширения продуктов сгорания свободнопоршневого энергомодуля с внешней камерой сгорания
EP3049672A1 (en) * 2013-09-24 2016-08-03 Optimol Tribotechnik S.A. Metering device for delivery of a liquid or viscous substance
RU2548704C1 (ru) * 2014-02-11 2015-04-20 Анатолий Александрович Рыбаков Способ оптимизации процесса расширения продуктов сгорания перепускными клапанами в цилиндрах свободнопоршневого с оппозитным движением поршней энергомодуля, соединенных с поршнями компрессора сжатия газов
RU2548528C1 (ru) * 2014-02-11 2015-04-20 Анатолий Александрович Рыбаков Способ оптимизации процесса расширения продуктов сгорания газораспределительными клапанами в цилиндрах свободнопоршневого с оппозитным движением поршней энергомодуля, соединенных с поршнями компрессора сжатия газов
EP4023854B1 (en) * 2018-01-15 2023-09-06 Graco Minnesota Inc. Compressed air driven motor
US20250035095A1 (en) * 2023-07-24 2025-01-30 Xiangzhi Li Pneumatic automatic reversing transfer pump

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US1406330A (en) * 1919-02-24 1922-02-14 John S Barner Engine
US2698517A (en) * 1952-05-21 1955-01-04 Kenneth F Witt Automatic means to control and reverse fluid-operated cylinder-and-piston units
US3405606A (en) * 1966-05-02 1968-10-15 Harry Kruger G M B H Control of double-acting pressure medium energized servo-motors
US3540349A (en) * 1965-05-20 1970-11-17 Hermann Joseph Pennther Fluid-operated continuously actuated reciprocating piston drive

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US1066483A (en) * 1912-07-17 1913-07-08 Frederick Randall Greene Fluid-pressure motor.
US1406330A (en) * 1919-02-24 1922-02-14 John S Barner Engine
US2698517A (en) * 1952-05-21 1955-01-04 Kenneth F Witt Automatic means to control and reverse fluid-operated cylinder-and-piston units
US3540349A (en) * 1965-05-20 1970-11-17 Hermann Joseph Pennther Fluid-operated continuously actuated reciprocating piston drive
US3405606A (en) * 1966-05-02 1968-10-15 Harry Kruger G M B H Control of double-acting pressure medium energized servo-motors

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3943823A (en) * 1974-06-13 1976-03-16 Nordson Corporation Control system for double acting air motor
EP0045536A1 (en) * 1980-08-04 1982-02-10 Manfred Berweger A multi-component delivery apparatus
US4398463A (en) * 1981-08-19 1983-08-16 Motter Printing Press Co. Non-repeat doctor blade drive
US4738107A (en) * 1983-04-22 1988-04-19 Carlander Lars Erik Device in an actuator for elevation adjustment of work stations
US5454290A (en) * 1992-10-15 1995-10-03 Bendix Espana S.A. Hydraulic control device with movable valve
US6398527B1 (en) * 2000-08-21 2002-06-04 Westport Research Inc. Reciprocating motor with uni-directional fluid flow
US6589027B2 (en) * 2000-08-21 2003-07-08 Westport Research Inc. Double acting reciprocating motor with uni-directional fluid flow
US20090211434A1 (en) * 2008-02-26 2009-08-27 Lauder Arthur W Fluid pressure powered apparatus
US20230046193A1 (en) * 2019-09-19 2023-02-16 Oshkosh Corporation Reciprocating piston pump
US11815078B2 (en) * 2019-09-19 2023-11-14 Oshkosh Corporation Reciprocating piston pump comprising a housing defining a first chamber and a second chamber cooperating with a first piston and a second piston to define a third chamber and a fourth chamber
US20240052818A1 (en) * 2019-09-19 2024-02-15 Oshkosh Corporation Reciprocating piston pump
US12404847B2 (en) * 2023-10-23 2025-09-02 Oshkosh Corporation Reciprocating piston pump

Also Published As

Publication number Publication date
FR2089004A5 (enrdf_load_stackoverflow) 1972-01-07
FR2092512A5 (enrdf_load_stackoverflow) 1972-01-21
GB1303004A (enrdf_load_stackoverflow) 1973-01-17
DE2015472A1 (de) 1971-10-07
GB1352068A (en) 1974-05-15
US3745886A (en) 1973-07-17

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