US3796136A - Fluid pump or fluid motor - Google Patents

Fluid pump or fluid motor Download PDF

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Publication number
US3796136A
US3796136A US00183324A US3796136DA US3796136A US 3796136 A US3796136 A US 3796136A US 00183324 A US00183324 A US 00183324A US 3796136D A US3796136D A US 3796136DA US 3796136 A US3796136 A US 3796136A
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United States
Prior art keywords
rear cover
valve plate
annular grooves
passages
annular
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Expired - Lifetime
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US00183324A
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English (en)
Inventor
H Oguni
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Kawasaki Heavy Industries Ltd
Kawasaki Motors Ltd
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Kawasaki Heavy Industries Ltd
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    • 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
    • F01B1/00—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements
    • F01B1/06—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements with cylinders in star or fan arrangement
    • F01B1/0675—Controlling
    • F01B1/0696—Controlling by changing the phase relationship between the actuating or actuated cam and the distributing means
    • 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
    • F01B1/00—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements
    • F01B1/06—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements with cylinders in star or fan arrangement
    • F01B1/0675—Controlling
    • F01B1/0679—Controlling by using a valve in a system with several pump or motor chambers, wherein the flow path through the chambers can be changed, e.g. series-parallel
    • 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
    • F01B13/00—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion
    • F01B13/04—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder
    • F01B13/06—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement
    • F01B13/061—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement the connection of the pistons with the actuated or actuating element being at the outer ends of the cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0403—Details, component parts specially adapted of such engines
    • F03C1/0435—Particularities relating to the distribution members
    • F03C1/0444—Particularities relating to the distribution members to plate-like distribution members

Definitions

  • ABSTRACT A fluid motor or fluid pump of the piston or vane type having a plurality of pistons or vanes, a mounting means for, said pistons or vanes, a cam ring, a rear cover, a valve plate interposed between said rear cover and said mounting means and a valve mounted outside of said rear cover.
  • a plurality of annular grooves having openings on an inner side surface of the rear cover are formed in said rear cover. Each groove has a port opening on outer side of the rear cover.
  • the valve plate with passages is disposed between the mounting means and the rear cover for covering said annular grooves and for communicating passages formed in said mounting means with said annular grooves.
  • a plurality of rings or inner and outer rings can be mounted for sliding contact with said valve plate.
  • An object of this invention is to provide a pressure distribution valve means for a fluid pump or fluid motor of the piston or vane type which is effective to vary the volume of effective working liquid for each revolution so as to permit the pump or motor to operate as a variable volume fluid pump or fluid motor.
  • Another object of the invention is to provide a working liquid distribution mechanism for a fluid pump or fluid motor which comprises a valve plate to accomplish the object.
  • FIG. 1 is a sectional view of a conventional motor or pump of the piston type
  • FIG. 2 and FIG. 3 are fragmentary sectional views taken along the lines XX and YYlY2-Y3Y4-Y5 of FIG. 1 respectively;
  • FIG. 4 is a sectional view of essential portions of the fluid pump or fluid motor according to the first embodiment of this invention.
  • FIG. 5 is a fragmentary sectional view taken along the line Z-Z of FIG. 4;
  • FIG. 6 and FIG. 7 are views in explanation of the operation of this invention.
  • FIG. 8 is a sectional view of essential portions of the fluid pump or motor according to the second embodiment of this invention.
  • FIG. 9, FIG. 10 and FIG. 11 are sectional views taken along the line X1X2-X3-X4-X5X6 of FIG. 8 and showing the parts in different states;
  • FIG. 12 is a vertical sectional view of essential portions of the fluid pump or motor according to the third embodiment of this invention.
  • FIG. 13 is a view in explanation of the arrangement of essential portions of FIG. 12 as seen from the right side.
  • FIG. 1 to FIG. 3 illustrate a fluid pump or fluid motor of the piston typeof the prior art. Essential portions of the device functioning as a fluid motor will be described.
  • a fluid under pressure supplied through a working fluid inlet port 1 passes through an annular passage 2, ducts 3, ports 5 formed in a valve plate 4 and passages 7 formed in a mounting means, for example, in a cylinder body 6 in the indicated order to move into cylinder chambers 8.
  • the working fluid in cylinder chambers 8 pushes and moves pistons 9 so as to bring rollers 10 mounted at the heads of pistons 9 into pressing engagement with a cam surface of a cam ring 20.
  • piston 90 will be pushed radially outwardly in a cylinder chamber 8a to rotate cylinder body 6 and a main shaft 14 in a section ranging from the lower dead point Al to an upper dead point B1.
  • the port 5 of valve plate 4 shown in FIG. 3 and the passage 7a in cylinder body 6 are maintained in communication with each other.
  • passage 7a in cylinder body is maintained in communication with the port 15 of valve plate 4 shown-in FIG. 3, and piston 9a is moved radially inwardly in cylinder chamber 8a so as to move the fluid in the cylinder chamber through port 15, duct 16 and annular passage 17 in the indicated order so as to discharge the fluid through an outlet port 18.
  • the fluid can be moved from an inlet port 18 to an outlet port 1 reversely.
  • an effective working fluid volume ql for each revolution of the motor can be expressed by the following formula:
  • ql 1r/4d -Z'S'm
  • d is the effective diameter of pistons
  • Z is the number of pistons
  • S is the stroke of pistons which may vary depending on the shape of the cam
  • m is the number of strokes of pistons for one revolution of motor (which is equal to the number of elevated portions of the cam).
  • ql is a constant and the motor is a constant volume motor.
  • the motor may be provided with four or six inlet and outlet ports and fluid may be supplied and discharged selectively through these ports by operation from outside so as to vary the number of effective working pistons.
  • this arrangement entails a complex valve and other switching mechanism which isdifficult to manufacture and troublesome to operate.
  • This invention obviates the aforementioned disadvantages of the prior art device described.
  • This invention is characterized in one aspect by the provision, as shown in FIGS. and 5, of inner and outer or two annular grooves 30 and 31 having openings on the inner side of rear cover 19, working liquid inlet and outlet ports 32 and 33 extending from the outer side of the rear cover to the bottoms of the respective annular grooves, a valve plate 34 positioned on one side against one side of cylinder body 6 and on the opposite side within an annular recess in the rear cover 19 extending across the annular grooves 30 and 31 and being slidable relative to the cylinder body, so as to provide a cover to the openings of the annular grooves, and a number of passages 35 and 36 formed in valve plate 34 so as to communicate a number of working liquid passages 7 with either of the two annular passages, said passages 7 opening in one side of cylinder body 6 to communicate with respective cylinder chambers 8.
  • annular grooves 30 and 31 according to this invention are not enclosed passages formed in rear cover 19 like annular passages 2 and 17 of the conventional device but are open on one side. This eliminates the use of a core in producing the rear cover in a molding operation. Annular grooves 30 and 31 can be formed by machining the rear cover after it is produced by casting in a mold.
  • the mechanism provided by this invention does without the ducts 3 and 16 of conventional device which are provided between the ports 5 and of valve plate 4 and annular passages 2 and 17 respectively. This eliminates the need to pay special attention to the flow of molten liquid in the molding operation.
  • passages 35 and 36 are provided in valve plate 34 in place of ducts 3'and 16, so that machining can be carried out positively by simple means.
  • valve plate 34 is slightly displaced peripherally with respect to the cylinder body of the motor, so that it is characterized by being able to regulate work output (volume) without influencing in any way the operation of switching work fluid which is the inherent function of the valve plate.
  • the ducts 35 and 36 in the valve plate are arranged such that, if the valve plate were mounted in its normal position, fluid under pressure would be supplied to the cylinder chambers when the pistons move from a lower dead point A to an upper dead point B of the cam surface, and the fluid in the cylinder chambers would be discharged therefrom when the pistons move from the upper dead point B to a next lower dead point C.
  • the output of the pistons at this time would be proportional to the hatched area in the figure.
  • valve plate 34 were displaced from its normal position such that the-supply of fluid under pressure to the cylinder chambers is initiated when the pistons are indexed with a point 01 disposed posterior to the lower dead point A and cut off when the pistons pass the upper dead point B and are indexed with a point 02 as shown in FIG. 7, the fluid under pressure would not perform outside work while the pistons move from A to 61 and would interfere with the introduction of the pistons into the respective cylinder chambers while the pistons move from B to 62 so that the output of the piston would be negative.
  • the aforementioned annular grooves and 31 may be modified such that, when cylinders are arranged in a plurality of rows disposed normal to the output (input) shaft or when effective volume is made variable while the cylinders are arranged in a single row, the number of annular grooves may be increased from one set to a plurality of sets, with one set being employed to close a set of passages to reduce the number of effectively working pistons.
  • the numeral 36' designates a channel interposed between annular grooves 30 and 31 opening at one end in the inner side of the rear cover.
  • Said channel 36 is normally maintained, through a small duct 37 in communication with one of the annular grooves 30 and 31 which is connected to the high pressure fluid side, so as to press against a back side of the valve plate a ring 38 mounted at the open end of said channel 36'.
  • ring 38 is pressed against the valve plate by virtue of pressure differential between the annular grooves 30 and 31, thereby preventing leakage of fluid.
  • the numeral 39 designates a contact plate mounted on the opening side of passages 11 through which part of the fluid under pressure in cylinder chambers 8 is led to a side of the cylinder body opposite to the side thereof on which valve plate 34 is disposed.
  • Contact plate 39 is intended to perform the function of pressing the cylinder body against valve plate 34 by virtue of the pressure of working fluid permitted to leak between contact plate 39 and
  • a clearance between the slide surfaces on the contact surfaces of the cylinder body 6 and the valve plate 34 and/or of the cylinder body 6 and the contact plate 39 can be optimally adjusted depending on the fluid pressure acting on the back surface of the valve plate 34. Therefore, leakage at the contact surfaces and seizure caused by metal contact can be prevented.
  • annular grooves and 131 are formed on an inner side of rear cover 19 to communicate with inlet and outlet ports 132 and 133 respectively which are formed on an outer side of the rear cover.
  • Annular grooves 130 and 131 have a common opening which is disposed on the inner side of rear cover 19 and covered with valve plate 134.
  • Rings 140 and 141 are mounted on outer and inner peripheral surfaces of a portion of valve plate 134 which projects into annular grooves 130 and 131, so that rings 140 and 141 can move in sliding motion in the respective grooves.
  • valve plate 134 and ducts (subsequently to be described) formed in ring 140 and 141 and/or passages 7 permits to vary the volume of effective working fluid of the motor as illustrated in FIGS. 9 to 11.
  • FIG. 9 shows the arrangement of the passages in the valve plate and the ducts in the inner and outer rings.
  • ducts 143 which are disposed in positions corresponding to one-half pitch of elevated portions of the cam surface and comprise a duct 143a aligned with the center line 0A1 of an elevated portion of the cam surface, a duct l43b aligned with the center line OBI of a depressed portion of the cam surface, and a duct 143C aligned with the center line 0A2 of an elevated portion of the cam surface.
  • valve plate 134 Formed in valve plate 134 are the passages 136a, a, 136b, 135b which are formed in the valve plate 134 to communicate with passages 7 on the cylinder body as shown in FIG. 8.
  • a passage 7 is indexed with the sage 7 is indexed with the passage 135a; and when it rotates through a section of the cam surface between 0A2 and next center line which is spaced apart from OA2 by one-half pitch of elevated portions of the cam surface, the particular passage 7 is indexed with the passage 136b.
  • duct 142d Formed in outer ring 140 in positions corresponding to elevated and depressed portions of the' cam surface in FIG. 9 are a duct 142d, duct 142a, recess 146, duct 142b and duct 142C in the indicated order.
  • the spacing between ducts l42dand 142a corresponds to one-half pitch of elevated portions of the cam surface; the spacing between ducts 142a and 14211 corresponds to one pitch of elevated portions of the cam surface; and recess 146 is disposed midway between ducts 142a and 142b or spaced apart from both ducts 142a and l42b a distance corresponding to one-half pitch of elevated portions of the cam surface, the recess 146 having an opening which is disposed adjacent an outer peripheral surface of valve plate 134.
  • each passage 136a, 136b, opened to the inner peripheral surface of the valve plate 134 opposed to the inner ring 141 the passages 135a, 135b, 1350 opened to the outer peripheral surface of the valve plate 134 opposed to the outer ring 140 are disposed as shown in FIG. 9.
  • the passage 135a is connected with one of the ducts 142 of the outer ring 140 and with one of the passages 7, while the passage 135b with two passages connected with each other is connected with the adjacent ducts 142 of the outer ring 140 and one of the common passages 7.
  • the passages 136a, 136b are formed with two passages connected with each'other at the opening communicated with-the passage 7, and are opened to the inner surface andthe outer surface of the valve plate 134.
  • the passages 1360, 136b and the passages l35a, 135b respectively are opened near to each other on the outer peripheral surface of valve plate 134 so as to connect each other at the recesses 146 of the outer ring.
  • the passages 1350, 135b and 1360, 13611 are so disposed that the passages 136a, 1361) are connected with the ducts 143a, 143C of the inner ring 141 respectively and the passage 7 in normal, that the passage 136a is connected with the duct 143d of the inner ring 141 and the passage 7, the passage 136b with the recess 146 of the outer ring 140 and with the, passage 7, the passage 135a with the duct 142d and with the passage 7 and the passage 135b with the recess 146, and the duct l42b of the outer ring 140 and with the passage 7, when the inner ring 141 and the outer ring 140 are rotated relatively to valve plate 134 from their positions in FIG.
  • the device operating as aforementioned functions as a motor of the constant volume type as is the case with the motor shown in' FIG. 1.
  • ducts 143b formed in inner ring 141 and shown in broken lines and ducts 142b formed in outer ring 140 and shown in broken lines are not put to service.
  • the aforementioned ducts are put to service when the device functions as a motor of the variable volume type as presently to be described.
  • FIG. 10 shows the motor in a state in which inner ring 141 and outer ring 140 are rotated relative to valve plate 134 from their positions in FIG. 9 in the direction of an arrow 0 a distance corresponding to one-half pitch of elevated portions of the cam surface and the port 133 is pressure supply side and the port 132 is pressure discharge side.
  • FIG. 11 shows the motor in a state in which the inner and outer rings are rotated in the opposite direction to that in FIG. 10, a distance corresponding to one-half pitch of elevated portions of the cam surface relative to FIG. 9 and the port 133 is connected to pressure discharge side and the port 132 is connected to pressure sage 1350 on the pressure supply side through a recess 146 so as to thereby shortcircuit the path of movement of working fluid.
  • the motor functions as a motor of the variable volume type.
  • the device shown in FIG. 8 is much easier to manufacture than the device shown in FIG. 1.
  • annular passages 2 and 17 and all the ducts leading from the annular passages to the velve plate should all be provided in the rear cover of the motor.
  • the inner and outer annular grooves have openings on the rear cover side so that the annular grooves in FIG. 8 are much easier to form by machining than the annular passages of FIG. 1 which are hidden in the rear cover and have no opening.
  • the valve plate can be readily worked on to form passages therein by machining. Formation of passages in the valve plate is thus much easier than formation of ducts in the rear cover which is produced by casting in a mold. I
  • the present embodiment has been described with reference to an embodiment which operates as a motor. It is to be understood, however, that the embodiment can be incorporated in a fluid pump with good results. The embodiment also can have application not only in motors and pumps of the radial piston type but also in motors and pumps ofthe axially piston type.
  • the annular grooves and inner and outer rings may be of different shape and arrangement than those shown and described herein depending on the type of motor or pump in which the invention is incorporated.
  • This invention also can have application with good results in the valve plate of a fluid device which is adapted to deliver fluid or do work by increasing and decreasing thevolume of an oil chamber surrounded by vanes.
  • the embodiment shown and described above permits to produce rear cover 19 more readily than in conventional fluid motors or pumps, and is effective to vary the volume of a motor or pump by rotating the valve plate 134.
  • a plurality of pairs of outlet and inlet portsand a plurality of pairs of annular grooves maintained in communication with the outlet and inlet ports are provided, so as to readily vary the volume of a motor or pump.
  • This embodiment permits to obtain a compact overall size in a fluid motor or pump in spite of the fact that a plurality of pairs of annular grooves are provided.
  • the openings of an inner pair of annular grooves on an inner surface of the rear cover and the openings of an outer pair of annular grooves on an inner surface of the rear cover are disposed in different planes. However, this is not essential and the openings may be disposed in the same plane.
  • two pairs of outlet and inlet ports 222, 225, and 228 and 231 are formed in rear cover 19 which are maintained in communication with two pairs of coaxial annular grooves 223, 226 and 229, 232.
  • the openings of annular grooves 223, 226 are formed in a position disposed deeper in the rear cover than the openings of annular grooves 229, 232.
  • the openings of these two pairs of annular grooves are closed by the outer side surface of valve plate 221 which is formed with a projection in the central portion and offset shoulders on opposite sides of the projection.
  • the valve plate is juxta'posed at its inner side surface with the side wall of the cylinder body 6.
  • ducts 224, 227, 230 and 233 are formed in the valve plate to maintain communication between the aforementioned annular grooves and the passage 7 formed in the cylinder body 6.
  • Each one of said ducts 224, 227, 230 and 233 is disposed between the elevated portion and the depressed portion of the cam surface.
  • the passages 7 are disposed for every cylinder chamber.
  • FIG. 13 shows the relative positions of passages 7 formed in cylinder body 6, ducts 230, 224, 227 and 233 formed in the valve plate for connecting passage 7 to annular grooves 229, 223, 226 and 232, and outlet and inlet ports 228, 222, 225 and 231 as seen from the right side of FIG. 12.
  • This embodiment has a plurality of pairs of annular grooves and a plurality of pairs of outlet and inlet ports as aforementioned.
  • a valve mountedoutside of this motor to use ports 228 and 225 as fluid supply ports or fluid dis charge ports and to use ports 222 and 231 as fluid discharge ports or fluid supply ports (first case) or to use ports 225 as a fluid supply or discharge port and to make the other ports 228 to communicate with port 231 so as to bypass the fluid while the port 222 is used as a discharge or supply port (second case).
  • a rate of the effective working fluid volume causing the pistons to operate will be 1 in the first case as against 0.5 in the second case.
  • a relation similar to the relation described above can be established by selecting any combination of two ports as desired from ports 231, 225, 222 and 228.
  • a fluid motor or fluid pump comprising a plurality of working members cooperating with a rotor member to form expansible working chambers therein, a cam ring located radially outwardly from said rotor member and having an inwardly facing cam surface arranged to cooperate with said working members, a rear cover mounted laterally of said rotor member and its said working chambers and extending transversely of the axis of the said rotor member, a valve plate mounted between said rear cover and said working chambers, said rear cover having an inner side surface extending transversely of the axis of said rotor member and facing toward said working chambers, and an outer side surface facing in the opposite direction, said rear cover having an annular recess in an inner side surface and a plurality of radially spaced annular grooves opening to said annular recess and disposed outwardly from said working chamber relative to said annular recess and having a plurality of working fluid outlet and inlet ports extending from said annular grooves to its outer side surface, said valve plate being

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
US00183324A 1970-09-24 1971-09-24 Fluid pump or fluid motor Expired - Lifetime US3796136A (en)

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JP1970094576U JPS4820082Y1 (enrdf_load_stackoverflow) 1970-09-24 1970-09-24

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US00183324A Expired - Lifetime US3796136A (en) 1970-09-24 1971-09-24 Fluid pump or fluid motor

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US (1) US3796136A (enrdf_load_stackoverflow)
JP (1) JPS4820082Y1 (enrdf_load_stackoverflow)
DE (1) DE2146844C3 (enrdf_load_stackoverflow)
FR (1) FR2112981A5 (enrdf_load_stackoverflow)
GB (1) GB1348157A (enrdf_load_stackoverflow)

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3949647A (en) * 1973-10-08 1976-04-13 Societe Anonyme: Poclain Hydraulic mechanism, such as a motor or a pump, having radial pistons adapted to perform a plurality of strokes per revolution
US4070950A (en) * 1974-12-12 1978-01-31 Cyphelly Ivan J Hydraulic apparatus including rotary valve
US4128048A (en) * 1975-12-27 1978-12-05 Teijin Seiki Company Limited Radial piston type hydraulic pump-motor
US4132154A (en) * 1975-12-27 1979-01-02 Teijin Seiki Company Limited Radial piston type hydraulic pump-motor
US4136602A (en) * 1976-05-24 1979-01-30 Lenz Leonard L Hydraulic motor
US5439356A (en) * 1993-04-13 1995-08-08 Sauer Inc. Hydraulic motor and pump having hydraulic counter balancing means
EP0974752A3 (en) * 1998-07-24 2000-10-04 RIVA CALZONI OLEODINAMICA S.p.A. Feedback control circuit for a variable speed hydromotor
EP1557562A1 (en) * 2004-01-23 2005-07-27 Jurij Manfreda Distributing system for a piston hydraulic engine
US20060055238A1 (en) * 2002-12-16 2006-03-16 Walker Frank H Hydraulic regenerative braking system for a vehicle
US20080185909A1 (en) * 2004-12-17 2008-08-07 Walker Frank H Hydraulic Regenerative Braking System For A Vehicle
US20080210500A1 (en) * 2005-05-11 2008-09-04 Walker Frank H Hydraulic Regenerative Braking System For a Vehicle
US20090223359A1 (en) * 2007-02-12 2009-09-10 Walker Frank H Hydraulic Machine Arrangement
US20090272343A1 (en) * 2008-05-05 2009-11-05 Man Nutzfahzeuge Oesterreich Ag Drive Unit with an Internal Combustion Engine and a Reciprocating Piston Engine which is Self-Starting without Regulation
US20100101406A1 (en) * 2007-02-12 2010-04-29 Walker Frank H Hydraulic machine arrangement

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3112931A1 (de) * 1981-03-31 1982-10-07 Joseph Vögele AG, 6800 Mannheim Radialkolbenpumpe
FR2661456B1 (fr) * 1990-04-26 1992-08-14 Poclain Hydraulics Sa Mecanisme a fluide sous pression, tel qu'un moteur ou une pompe hydraulique, a plusieurs cylindrees de fonctionnement.
WO2024225114A1 (ja) * 2023-04-28 2024-10-31 カヤバ株式会社 液圧回転機

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US2712794A (en) * 1949-06-15 1955-07-12 Marion W Humphreys Fluid motor or pump
US3086477A (en) * 1960-05-09 1963-04-23 New York Air Brake Co Variable displacement pump
US3206218A (en) * 1959-01-14 1965-09-14 Sperry Rand Corp Power transmission
US3362342A (en) * 1964-06-12 1968-01-09 Dowty Technical Dev Ltd Hydraulic apparatus
US3435775A (en) * 1967-11-13 1969-04-01 Benton Harbor Eng Works Inc Hydraulic pump or motor

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2712794A (en) * 1949-06-15 1955-07-12 Marion W Humphreys Fluid motor or pump
US3206218A (en) * 1959-01-14 1965-09-14 Sperry Rand Corp Power transmission
US3086477A (en) * 1960-05-09 1963-04-23 New York Air Brake Co Variable displacement pump
US3362342A (en) * 1964-06-12 1968-01-09 Dowty Technical Dev Ltd Hydraulic apparatus
US3435775A (en) * 1967-11-13 1969-04-01 Benton Harbor Eng Works Inc Hydraulic pump or motor

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3949647A (en) * 1973-10-08 1976-04-13 Societe Anonyme: Poclain Hydraulic mechanism, such as a motor or a pump, having radial pistons adapted to perform a plurality of strokes per revolution
US4070950A (en) * 1974-12-12 1978-01-31 Cyphelly Ivan J Hydraulic apparatus including rotary valve
US4128048A (en) * 1975-12-27 1978-12-05 Teijin Seiki Company Limited Radial piston type hydraulic pump-motor
US4132154A (en) * 1975-12-27 1979-01-02 Teijin Seiki Company Limited Radial piston type hydraulic pump-motor
US4136602A (en) * 1976-05-24 1979-01-30 Lenz Leonard L Hydraulic motor
US5439356A (en) * 1993-04-13 1995-08-08 Sauer Inc. Hydraulic motor and pump having hydraulic counter balancing means
US5697286A (en) * 1993-04-13 1997-12-16 Sauer Inc. Fluid pressure unit with brake means
US5697765A (en) * 1993-04-13 1997-12-16 Sauer Inc. Hydraulic motor
EP0974752A3 (en) * 1998-07-24 2000-10-04 RIVA CALZONI OLEODINAMICA S.p.A. Feedback control circuit for a variable speed hydromotor
US20060055238A1 (en) * 2002-12-16 2006-03-16 Walker Frank H Hydraulic regenerative braking system for a vehicle
US7562944B2 (en) 2002-12-16 2009-07-21 Walker Frank H Hydraulic regenerative braking system for a vehicle
US20090236906A1 (en) * 2002-12-16 2009-09-24 Walker Frank H Hydraulic Regenerative Braking System For A Vehicle
EP1557562A1 (en) * 2004-01-23 2005-07-27 Jurij Manfreda Distributing system for a piston hydraulic engine
US20080185909A1 (en) * 2004-12-17 2008-08-07 Walker Frank H Hydraulic Regenerative Braking System For A Vehicle
US8132868B2 (en) 2004-12-17 2012-03-13 Walker Frank H Hydraulic regenerative braking system for a vehicle
US20080210500A1 (en) * 2005-05-11 2008-09-04 Walker Frank H Hydraulic Regenerative Braking System For a Vehicle
US20090223359A1 (en) * 2007-02-12 2009-09-10 Walker Frank H Hydraulic Machine Arrangement
US20100101406A1 (en) * 2007-02-12 2010-04-29 Walker Frank H Hydraulic machine arrangement
US8162621B2 (en) 2007-02-12 2012-04-24 Walker Frank H Hydraulic machine arrangement
US8176838B2 (en) 2007-02-12 2012-05-15 Walker Frank H Hydraulic machine arrangement
US20090272343A1 (en) * 2008-05-05 2009-11-05 Man Nutzfahzeuge Oesterreich Ag Drive Unit with an Internal Combustion Engine and a Reciprocating Piston Engine which is Self-Starting without Regulation
US8201407B2 (en) * 2008-05-05 2012-06-19 Man Truck & Bus Ag Drive unit with an internal combustion engine and a reciprocating piston engine which is self-starting without regulation

Also Published As

Publication number Publication date
FR2112981A5 (enrdf_load_stackoverflow) 1972-06-23
DE2146844B2 (de) 1979-02-08
JPS4820082Y1 (enrdf_load_stackoverflow) 1973-06-09
DE2146844C3 (de) 1979-09-27
DE2146844A1 (de) 1972-03-30
GB1348157A (en) 1974-03-13

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