US3873240A - Hydraulic swash plate pump - Google Patents

Hydraulic swash plate pump Download PDF

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Publication number
US3873240A
US3873240A US370545A US37054573A US3873240A US 3873240 A US3873240 A US 3873240A US 370545 A US370545 A US 370545A US 37054573 A US37054573 A US 37054573A US 3873240 A US3873240 A US 3873240A
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Prior art keywords
jack
pump
delivery
pump according
pressure
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Expired - Lifetime
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US370545A
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English (en)
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Gerard Leduc
Michel Leduc
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Priority claimed from FR7221752A external-priority patent/FR2190173A5/fr
Priority claimed from FR7238168A external-priority patent/FR2205114A6/fr
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    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/18—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders having self-acting distribution members, i.e. actuated by working fluid
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26—Control
    • F04B1/28—Control of machines or pumps with stationary cylinders
    • F04B1/29—Control of machines or pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B1/295—Control of machines or pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
    • 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
    • F04B49/08—Regulating by delivery pressure

Definitions

  • ABSTRACT Swash plate pump comprising a rotatable swash plate 52 us. (:1. 417/222, 417/270 the inclination of which is Controlled y a hydraulic 1511 Int. Cl.
  • F04b 49/00 j means The l means is in win Controlled y 11 [58] Field of Sear h 417/212 218 222 270; slide valve which detects the variations in the delivery 91/506; 60/452 pressures of the pump and causes a high or a low pressure to actuate the jack means, whereby the inclina- [56] References Ci d tion of the swash plate is modified and consequently 1E6 output Of thebpump The S11C1 VLliVC fur- 3.835228 /1958 Parr et a1.
  • the present invention relates to improvements in hydraulic pumps of variable cubic capacity and particularly to pumps of the type such as described in US. Pat. No. 3,575,534 and having as its title Constant torque hydraulic pump.
  • the pump described in this patent is a pump having a rotatable swash plate, of which the inclination is modified by means of a hydraulic jack, of
  • the present invention concerns a pump operating by the same general principle, but comprising a distribution system which is considerably improved as compared with that described in US. Pat. No. 3,575,534 of Feb. 5, 1969.
  • pumps providing separate rates of flow are being used to an ever-increasing extent: for example, with a pump having six pistons, it is possible to split up the flow of the pump into two separate flows, each supplied by three pistons, or even with a pump having nine pistons, into three flows each supplied by three pistons. It is quite obvious that, in these cases, it is necessary to have a valve capable of forming the sum of the pressures obtaining in the three circuits so as to act as a function of the torque necessary for driving the pump.
  • Another object of the invention is to permit the manufacture of the pumps to be standardised, a single pump head being capable of being used with different bodies having three, or six, or nine pistons.
  • a last object of the invention is to permit the supply of the pump to be achieved by an axial bore in the pump body, this considerably improving the volumetric yield thereof, but is not possible with a pump such as that which is described in US. Pat. No. 3,575,534.
  • FIG. 1 is a longitudinal section of a pump with 6 pis tons, in accordance with the invention
  • FIG. 2 is a partial view, as a longitudinal section along a plane perpendicular to the sectional plane of FIG. 1, in which a single piston is represented and this piston is offset by one-twelth of a revolution, so that the FIGURE may be more clear;
  • FIG. 3 is a partial view illustrating a modified form of the valve in FIG. 1;
  • FIG. 4 is a top plan view of the swash plate of FIG.
  • FIG. 5 is a partial view of FIG. 1, illustrating the swash plate in the position which it occupies when the delivery is zero;
  • FIG. 6 is a sectional view along AA of FIG. 5;
  • FIG. 7 is a partial view,'as a section BB of FIG. 6;
  • FIG. 8 is a partial view, as a section CC of FIG. 6;
  • FIG. 9 is a longitudinal sectional view along the line AA of FIG. 10 of a 12-piston pump, grouped into four deliveries, comprising the improvements according to the present addition;
  • FIG. 10 is a sectional view along the line BB of FIG. 9;
  • FIG. 11 is a partial view as a longitudinal section of a pump similar to that of FIG. 9, comprising a modification
  • FIG. 12 is a sectional view along the line DD of FIG. 11.
  • the pump is in two parts: the pump body 1, comprising the pumping pistons 3, and the pump head 2, comprising the driving shaft 4 which, by means of a pin 5, supports the swash plate 6.
  • the shaft 4 is driven in rotation by a motor (not shown) it drives the swash plate 6, which alternately pushes back the pistons 3, which are countersupported by springs 7.
  • the'swash plate 6 is pivoted on a pin 5, its inclination can be modified, the travel of the pistons 3 decreasing as a function of the decrease in the angle of the plate 6.
  • the modifications in the inclination of the plate 6 are caused by a hydraulic jack formed by a piston 8 sliding in a bore 8a drilled axially in the shaft 4 and possibly provided with a sleeve or liner 812, so that during operation, the plate receives the thrust of the pistons 3 on one side and thrust of the piston 8 on the other side.
  • the thrust exerted by the front face of the plate is alternately caused by two or three pistons, and the result thereof is a high frequency pulsation of the pressure obtaining at the rear of the piston 8, which pulsation cancels out the frictional effects of the various movable elements of the system.
  • the thrust experienced by the front face of the swash plate oscillates by 2.5 i 20%, and this, when the shaft 4 is turning at 1,500 rpm, corresponds to a pulsation at a frequency of 250 cycles per second.
  • the swash plate 6 When there is an even number of pistons 3, for example, six pistons, and when the pump is a double-acting pump, the swash plate 6 also experiences high frequency pressure pulsations when the two deliveries are not at the same pressure. When the two deliveries are at the same pressure, or when the pump has a single delivery, there is also a high frequency pulsation which arises from the fact that, because of compressibility phenomena which are shown at the pressures under consideration, the travel of the pistons with a rise in pressure is not symmetrical with that with a fall in pressure, relatively to the line of maximum slope of the plate.
  • the swash plate 6 comprises a central blind hole 9 which communicates by way of a passage 10 with a crescent-shaped passage 11, over which the studs 12 of the pistons 3 pass at the time of rotation of the plate 6.
  • the pistons 3 are in their suction stroke and the liquid surrounding the plate 6 in the chamber 13 is drawn into the bores in which the said pistons 3 are sliding.
  • a plurality of bores 14 have been placed along the path traversed by the studs 12 in the part corresponding to the delivery, each bore being provided with a non-return valve and communicating with a central chamber 16 which is drilled in the rear face of the swash plate 6 (FIG. 2).
  • the bores 14 are spaced from one another at a distance such that any one stud of a group of studs corresponding to a rate of flow always has its central orifice communicating with a bore.
  • the pin 5 on which the swash plate 6 is pivoted comprises along its longitudinal axis a duct 34 which communicates with the said chamber 16 through a duct 35 and a passage 35a, drilled in the body of the swash plate 6.
  • a duct 34 which communicates with the said chamber 16 through a duct 35 and a passage 35a, drilled in the body of the swash plate 6.
  • the passages 36 are directed towards the face of the plate 6, against which the pistons 3 are adapted to bear, and the passages 37 are directed towards the face of the plate 6, against which the piston 8 is bearing.
  • the purpose of this lack of symmetry is to balance at least partially the torsional force to which the pin 5 is subjected, because the force of the pistons 3 on the plate 6 is unsymmetrical.
  • the chamber 13 is supplied with liquid originating from a reservoir through a duct 17 in the pump body 1 along the axis of this latter, this being favourable to the supply of the blind hole 9 and consequently of the crescent-shaped passage 11.
  • the piston 8 bears against the rear face of the swash plate 6 by means of a stud 18 which covers the chamber 16.
  • This stud 18 comprises an annular recess 19 facing the plate 6 and an annular recess 20 facing the spherical head of the piston 8. These two recesses are supplied with oil under pressure coming from the chamber 16 through a conduit 21 comprising a calibrated passage 22.
  • the piston 8 is extended at its rear end by a rod 24 which slides in a bore 25 which discharges into a chamber 26 closed by a plug 27.
  • the rod 24 comprises a cylindrical shoulder 24a which, with the bore 25, defines an annular calibrated passage of variable length.
  • the said piston 8 carries a valve which receives the high pressure and the low pressure and which causes one or the other to communicate with the said chamber 23 for actuating the piston 8 in one direction or the other, so as to modify the inclination of the swash plate 6 and hence to adapt the rate of flow delivered by the pump.
  • this valve is formed by a slide valve 29 which slides in a bore 28 formed in the rod 24 and the piston 8, the said valve being countersupported by a spring 30.
  • the slide valve 29 comprises an annular chamber 29a, into which discharges a conduit 31 communicating with the chamber 23; with the displacement of the slide valve 29, this chamber is capable of being brought into communication either with the chamber 16 at high pressure, by means of the conduit 32, or with the chamber 13 at low pressure, by means of the conduit 33.
  • FIG. 1 When the shaft 4 is stationary, the parts in the position which is shown in FIG. 1; on the other hand, FIG. 2 illustrates the parts in an equilibrium position.
  • the swash plate 6 receives on one face a thrust which is caused by the pistons 3, which thrust is balanced by that of the piston 8. If the outlet pressures (in the case of a pump with 2 x 3 pistons delivering two independent rates of flow) are called P, and P and ifs is the total section of the piston 8, the balancing pressure p in the chambers 23 and 26 is a function of P, and P in the form:
  • non-return devices 15 will be noted, this being to select the higher of the two pressures P, and P for supplying the valve and thus to permit that a displacement of the piston 8 is always able to correspond to a displacement of the said valve.
  • the thrust on the plate 6 likewise increases, and this has the effect of increasing the balancing pressure p in the chambers 23 and 26.
  • the effect of the increase in the pressure in the chamber 26 is to drive in the slide valve 29, which brings the conduits 32 and 31 into communication, in such a way that the high pressure obtaining in the chamber 16 is directed into the chamber 23.
  • the piston 8 then starts to be displaced towards the right at a speed determined by the speed at which the slide valve is driven in, this movement of said valve being continued as long as there is lack of equilibrium between the pressure in the chamber 26 and the action of the spring 30.
  • the volume of the chamber 26 increases.
  • the delivery which is necessary for making good this increase in volume is proportional to the speed of the jack.
  • This delivery or flow comes from the chamber 23, while undergoing a pressure drop through the calibrated orifice 24a, this drop in pressure being proportional to the said flow, that is to say, to the speed of the jack.
  • the signalling pressure in the chamber 26, which was p in the state of equilibrium and which was changed to, shall we say, p, because of the increase in P, or P is thus lowered in proportion as the slide valve moves inwardly and the jack is accelerated. However, all this has taken place over approximately a few hundredths of millimetres.
  • the spring 30 is calibrated so as to balance this pressure of 242.7 bars which is acting on the slide valve 29.
  • the spring can be a single spring or there may be several separate springs or even springs in two groups: one between the slide valve 29 and the shaft 4, the spring 30, and the other between the slide valve 29 and the rod 24, as is shown in FIG. 3, this being the spring 30a.
  • EXAMPLE A double delivery pump has been developed which comprises six equal pistons 3 with a diameter of 31.00 mm, delivering at maximum cubic capacity (maximum inclination of the plate 6) two equal rates of flow of 50 cc/revolution.
  • the piston 8 has a diameter of 60 mm
  • the rod 24 has a diameter of 18 mm
  • the slide valve 29 a diameter of 6 mm.
  • the pressure drop in the calibration 24a is thus 264.7 242.7 22 bars and the speed of the piston 8 is proportional to this quantity.
  • the calibration 240 makes it possible to obtain a very good control of the speed of the piston 8 as a function of the error remaining to be made good, that is to say, a very good damping of the readjustments which are constantly necessary in order to maintain the selected relationship between the cubic capacities and the pressures.
  • FIGS. 9 to 12 relate to a modified constructional form concerned with the means for permitting the selection of the highest of the delivery pressures and of directing it on to the control valve.
  • the valve receives the high pressure through the conduit 32 which discharges at the middle of the bearing stud 18, which encloses the chamber 16 in which obtains the highest of the delivery pressures.
  • the strongest delivery pressure is selected by non-return valves 40 placed in the pump body 1 immediately downstream of the pistons 3.
  • the pump comprises 12 pistons 3 which are grouped in threes so that the pump has four independent delivery flows: the first delivery is supplied by the pistons 3a, the second by the pistons 3b, the third by the piston 30 and the fourth by the pistons 3d; the deliveries of the pistons of a single group are connected with one another downstream of the non-return valves 42a, 42b, 42c, 42:] by conduits 41, such as 41a for the pistons 3a.
  • the delivery of the group a is thus taken by the nonreturn valve 40a, that of the group b by the non-return valve 40b, and so on, and downstream of the closure member, the non-return valves 40a, 40b, 40c and 40d are interconnected by a conduit 43.
  • the pressure obtaining in the conduit 43 is always the highest of the four delivery pressures.
  • This pressure is carried through a conduit 44 drilled in the casing 1-2 of the pump as far as a passage 45 drilled in the jack 8, opening on to the slide member 29 of the valve.
  • connection between the passage 44 and the passage 45 is obtained by means of a rotating joint formed by a ring 46 mounted with friction on the shaft 4, the said ring 46 being immobilised by a stop member 47.
  • the chamber 29a of the slide valve 29 communicates, by means of the passage 31, firstly with the chamber 23 situated behind the jack and, secondly, with the central space of the supporting stud 18'.
  • This supporting stud 18 is preferably biconical and receives, on the one hand, the spherical head of the jack 8 and, on the other hand, the spherical part of a hub 48 placed at the back of the swash plate 6. Formed in the body of this hub 48 is a passage 35a which communicates with the passage 35.
  • the pressure obtaining inside the stud 18 is always the highest of the delivery pressures, and this makes necessary the determination of the contact circle between jack 8 and stud 18 as a function of the highest possible delivery pressure, and the result of this is a hydraulic over-balancing of the bearing of the jack on its stud; this over-balancing necessitates the presence of a calibrated leakage flow device, such as that bearing the references 19 to 22.
  • FIGS. 11 and 12 show a modified form of the system for selecting delivery pressures.
  • the non-return valves 40 are placed upstream in the chambers of the pistons 3, and no longer downstream of the non-return valves 42.
  • references 30 and 3a no longer designate the delivery pistons of the pump, but the bores in which the said pistons slide.
  • a hydraulic swash plate pump whose driving torque is to be kept constant as a function of delivery pressure, said pump comprising:
  • control means having first and second inlets and an outlet, means for providing fluid at the delivery pressure to said first inlet and means for providing low pressure fluid to said second inlet,
  • control means including a chamber in fluid communication with said jack and responsive to an applied fluid to move said control means
  • control valve means communicating between said control valve means outlet and said jack moving means, said control valve means moving in response to variation of pressure in said chamber and communicating the fluid from one of said first or second inlets to said outlet to move said jack in a direction to change the inclination of the swash plate to maintain a given torque at said driving means in response to a variable delivery pressure, said control valve means also being movable with respect to said jack to vary the flow of the fluid to said jack as the jack moves.
  • control means includes a slide valve communicating with and responsive to the pressure in said chamber (26-26) and further comprising spring means for exerting a force on said slide valve means in opposition to the force exerted thereon by the fluid in said chamber.
  • control means comprises a valve located inside the jack.
  • the jack includes a piston having a surface communicating with said chamber, said piston of the jack controlling the swash plate having a double section of different sizes, said jack moving means including two chambers situated so that one communicates with the large section and the other communicates with the small section of said jack piston, a calibrated passage means providing communication between said two chambers, the chamber situated behind the large section receiving either the high pressure or the low pressure by means of the valve, so that, with equilibrium, the said valve being closed, these two chambers are at the same pressure, which is a function of the delivery pressure.
  • the jack includes a rod having a shoulder extending through said orifice such that the said annular calibrated passage is of variable length.
  • said jack having a piston including a supporting stud for providing communication between said central chamber and a passage formed in the said piston and ending at the valve.
  • Pump according to claim 13 further comprising selection non-return valves for all the delivery systems of the pump.
  • Pump according to claim 1 further comprising first means for applying the highest selected delivery pressure to the valve positioned inside the jack by means, said first means comprising a passage drilled in the casing of the pump body and a passage drilled in the jack.
  • Pump according to claim 18, further comprising ajoint between two passages, said joint including a ring which is centered with friction on the jack and is held immobile to rotation, said ring having a passage providing communication between the said two passages.
  • Pump according to claim 14 further comprising selection non-return valves for all the delivery systems of the pump.
  • Pump according to claim 14 further comprising a selection non-return valves for providing a single delivery by flow.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
US370545A 1972-06-16 1973-06-15 Hydraulic swash plate pump Expired - Lifetime US3873240A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR7221752A FR2190173A5 (enrdf_load_stackoverflow) 1972-06-16 1972-06-16
FR7238168A FR2205114A6 (enrdf_load_stackoverflow) 1972-10-27 1972-10-27

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US3873240A true US3873240A (en) 1975-03-25

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US370545A Expired - Lifetime US3873240A (en) 1972-06-16 1973-06-15 Hydraulic swash plate pump

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US (1) US3873240A (enrdf_load_stackoverflow)
JP (1) JPS4963003A (enrdf_load_stackoverflow)
DE (1) DE2330607A1 (enrdf_load_stackoverflow)
GB (1) GB1436390A (enrdf_load_stackoverflow)

Cited By (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4137013A (en) * 1977-09-22 1979-01-30 The Bendix Corporation Variable displacement piston pump
US4149830A (en) * 1977-05-16 1979-04-17 The Bendix Corporation Variable displacement piston pump
US4229144A (en) * 1978-12-07 1980-10-21 Deere & Company Feedback shaft extending between swashplate and displacement control valve
US4255092A (en) * 1977-11-24 1981-03-10 Plessey Handel Und Investments Ag Hydraulic variable-displacement axial piston pump having torque limitation
US4294139A (en) * 1979-01-05 1981-10-13 U.S. Philips Corporation Drive for a machine comprising variable-stroke reciprocating pistons
USRE31107E (en) * 1978-12-07 1982-12-21 Deere & Company Feedback shaft extending between swashplate and displacement control valve
US4597483A (en) * 1981-11-30 1986-07-01 Hydro Rene Allee Rene Leduc Azerailles Hydrostatic clutch
US4703682A (en) * 1985-06-03 1987-11-03 Danfoss A/S Varible displacement piston pump or motor
US4793774A (en) * 1987-09-28 1988-12-27 Allied-Signal Inc. Variable displacement high pressure pump
US5440878A (en) * 1992-08-27 1995-08-15 Vernon E. Gleasman Variable hydraulic machine
US5836748A (en) * 1994-07-13 1998-11-17 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate type variable displacement compressor utilizing a spool for controlling the inclination
US5931644A (en) * 1995-03-30 1999-08-03 Caterpillar Inc. Precision demand axial piston pump with spring bias means for reducing cavitation
DE29914763U1 (de) * 1999-08-24 2001-01-04 Connectool GmbH & Co., 32758 Detmold Zange
US6264437B1 (en) * 1996-06-07 2001-07-24 Hydro Rene Leduc High pressure pump for all liquids
US20030002990A1 (en) * 2001-06-27 2003-01-02 Klaus Reitzig Multi-cylinder high-pressure plunger pump
US20030001705A1 (en) * 2001-06-25 2003-01-02 Toshiki Sugiyama Combination switch
US20040096335A1 (en) * 2002-11-15 2004-05-20 Caterpillar, Inc. Hydraulic pump housing
US20040131473A1 (en) * 2003-01-03 2004-07-08 Lavorwash S.P.A. Motor pump for high-pressure washers with automatically variable flow-rate and pressure
CN102720648A (zh) * 2012-05-29 2012-10-10 华中科技大学 一种全深度浮力调节海水泵
US9909576B2 (en) * 2015-01-23 2018-03-06 Caterpillar Inc. Pump drive system with hydraulic tappets
US20180223816A1 (en) * 2014-12-01 2018-08-09 Fna Group, Inc. Pump
CN114320805A (zh) * 2021-12-21 2022-04-12 北京华德液压工业集团有限责任公司 轴向液压泵的柱塞结构及包括其的轴向液压泵
WO2022172099A1 (en) * 2021-02-11 2022-08-18 Mixtron S.R.L. Axial pump with inclined plate
KR20230103017A (ko) * 2021-12-30 2023-07-07 성보 피앤티 주식회사 서지 압력의 완화 기능이 우수한 사판식 유압펌프
US20250188913A1 (en) * 2022-03-31 2025-06-12 Kawasaki Jukogyo Kabushiki Kaisha Rotary swash plate hydraulic pump
US20250207569A1 (en) * 2022-03-31 2025-06-26 Kawasaki Jukogyo Kabushiki Kaisha Rotary swash plate hydraulic pump

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1568946A (en) * 1977-05-09 1980-06-11 Bendix Corp Variable displacement piston pump
JPS60187780A (ja) * 1984-03-07 1985-09-25 Hitachi Ltd 回転斜板式可変ポンプ
JPH0223829Y2 (enrdf_load_stackoverflow) * 1987-05-19 1990-06-28
JPH0413425Y2 (enrdf_load_stackoverflow) * 1988-04-28 1992-03-27
JPH0489873U (enrdf_load_stackoverflow) * 1990-12-15 1992-08-05
JPH05312144A (ja) * 1992-05-08 1993-11-22 Sanden Corp 可変容量斜板式圧縮機

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Publication number Priority date Publication date Assignee Title
US2835228A (en) * 1954-12-07 1958-05-20 American Brake Shoe Co Pressure compensator for variable volume pumps
US3304886A (en) * 1965-11-12 1967-02-21 Borg Warner Variable displacement check valve pump
US3512178A (en) * 1967-04-24 1970-05-12 Parker Hannifin Corp Axial piston pump
US3575534A (en) * 1968-02-07 1971-04-20 Gerard Leduc Constant torque hydraulic pump
US3588286A (en) * 1969-06-20 1971-06-28 Lucas Industries Ltd Control systems for hydraulic pumps

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2835228A (en) * 1954-12-07 1958-05-20 American Brake Shoe Co Pressure compensator for variable volume pumps
US3304886A (en) * 1965-11-12 1967-02-21 Borg Warner Variable displacement check valve pump
US3512178A (en) * 1967-04-24 1970-05-12 Parker Hannifin Corp Axial piston pump
US3575534A (en) * 1968-02-07 1971-04-20 Gerard Leduc Constant torque hydraulic pump
US3588286A (en) * 1969-06-20 1971-06-28 Lucas Industries Ltd Control systems for hydraulic pumps

Cited By (32)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4149830A (en) * 1977-05-16 1979-04-17 The Bendix Corporation Variable displacement piston pump
US4137013A (en) * 1977-09-22 1979-01-30 The Bendix Corporation Variable displacement piston pump
US4255092A (en) * 1977-11-24 1981-03-10 Plessey Handel Und Investments Ag Hydraulic variable-displacement axial piston pump having torque limitation
US4229144A (en) * 1978-12-07 1980-10-21 Deere & Company Feedback shaft extending between swashplate and displacement control valve
USRE31107E (en) * 1978-12-07 1982-12-21 Deere & Company Feedback shaft extending between swashplate and displacement control valve
US4294139A (en) * 1979-01-05 1981-10-13 U.S. Philips Corporation Drive for a machine comprising variable-stroke reciprocating pistons
US4597483A (en) * 1981-11-30 1986-07-01 Hydro Rene Allee Rene Leduc Azerailles Hydrostatic clutch
US4703682A (en) * 1985-06-03 1987-11-03 Danfoss A/S Varible displacement piston pump or motor
US4793774A (en) * 1987-09-28 1988-12-27 Allied-Signal Inc. Variable displacement high pressure pump
US5440878A (en) * 1992-08-27 1995-08-15 Vernon E. Gleasman Variable hydraulic machine
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Also Published As

Publication number Publication date
GB1436390A (en) 1976-05-19
DE2330607A1 (de) 1974-01-10
JPS4963003A (enrdf_load_stackoverflow) 1974-06-19

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