US3828400A - Hydraulic motors and the like - Google Patents

Hydraulic motors and the like Download PDF

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US3828400A
US3828400A US00221366A US22136672A US3828400A US 3828400 A US3828400 A US 3828400A US 00221366 A US00221366 A US 00221366A US 22136672 A US22136672 A US 22136672A US 3828400 A US3828400 A US 3828400A
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United States
Prior art keywords
eccentric
shaft
hydraulic motor
drive
motor
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US00221366A
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English (en)
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B Mason
M Young
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Chamberlain Industries Ltd
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Chamberlain Industries Ltd
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    • 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
    • F03C1/0447—Controlling
    • F03C1/0457—Controlling by changing the effective piston stroke
    • F03C1/046—Controlling by changing the effective piston stroke by changing the excentricity of one element relative to another element
    • 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
    • F04B49/123—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 by changing the eccentricity of one element relative to another element
    • F04B49/125—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 by changing the eccentricity of one element relative to another element by changing the eccentricity of the actuation means, e.g. cams or cranks, relative to the driving means, e.g. driving shafts
    • 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
    • F03C1/053—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement the pistons co-operating with an actuated element at the inner ends of the cylinders
    • F03C1/0538—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement the pistons co-operating with an actuated element at the inner ends of the cylinders the piston-driven cams being provided with inlets or outlets
    • 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
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/06—Control
    • F04B1/07—Control by varying the relative eccentricity between two members, e.g. a cam and a drive shaft

Definitions

  • ABSTRACT A radial-cylinder hydraulic motor in which a series of reciprocating pistons are arranged around an eccentric mounted on a drive shaft, has a novel eccentric construction, the eccentric comprising an annulus which is driven by the pistons, and opposed pistonand-cylinder devices which are based on said drive shaft carry the annulus towards and away from the axis of the drive shaft to vary the throw of the eccentric and thus the displacement of the motor.
  • the piston-and-cylinder device which moves the annulus away from the shaft axis is preferred to have a larger effective working area than the piston-and-cylinder device which moves the annulus towards the shaft axis.
  • This invention relates to a variable-throw eccentric device which has particular application to slow-speed radialcylinder hydraulic motors.
  • Hydraulic motors of the radial-cylinder type such as de cribed in the specification of our British Pat. No. l,085,232 and marketed under our Trade Mark STAFFA, are usually powered by means of a pump driven by an electrical motor. It is possible to vary the speed and the power output of the motor by varying the delivery (i.e., the displacement) of the pump, but this involves the provision of a relatively large and expensive pump to provide adequate low-pressure delivery for motor conditions of high speed and low torque. The size of pump could, however, be reduced if the motor displacement could be varied, and it is an object of the present invention to provide a means for satisfactorily varying the motor displacement.
  • a radial-cylinder hydraulic motor in which a series of reciprocatory pistons are arranged around an eccentric mounted on a drive shaft, characterised in that said eccentric comprises an annulus in driving connection with said pistons, and opposed hydraulically-operated piston and cylinder devices based on the drive shaft carry the annulus towards and away from the axis of the shaft to vary the throw of the eccentric and thus the displacement of the motor.
  • the annulus tends to move to a position of maximum eccentricity; thus, it is desirable to increase the effective working area of the piston and cylinder device which acts to move the annulus towards the shaft axis.
  • the throw may be infinitely variable, or the annulus may be movable between two positions such as high and low or, alternatively, drive and neutral.
  • the neutral position may be employed to allow freewheeling of the shaft, for example where free-fall is required in winching operations.
  • the annulus may be movable past the neutral (zero-stroke) position, thus enabling the motor to reverse rotation without altering the direction of supply of fluid flow. This would simplify some hydraulic circuits by the elimination of costly control valves.
  • the present invention is also applicable to radial-cylinder hydraulic pumps, and it is envisaged that the invention may have wider application, for example to steam engines, air compressors or other reciprocating mechanisms.
  • the invention provides a hydraulic machine in which at least one reciprocatory piston is arranged in driving engagement with an eccentric mounted on a drive shaft, characterised in that said eccentric comprises an annulus in driving connection with said piston, and opposed hydraulically-operatedpiston and cylinder means based on the drive shaft are arranged to carry the annulus towards and away from the axis of the drive shaft to vary the throw of the eccentric and thus the displacement of the machine.
  • FIGS. 1 and 2 are axial and transverse sectional views, respectively, showing one form of variablestroke hydraulic motor crank-shaft with its twoposition eccentric in the full-stroke position;
  • FIG. 3 is a view corresponding to FIG. 1, but showing the zero-stroke position of the eccentric
  • FIG. 4 is an axial sectional view showing a radialcylinder hydraulic motor incorporating a crankshaft as shown in FIGS. 1 and 2;
  • FIG. 5 is a diagrammatic sectional view showing a DESCRIPTION OF PREFERRED EMBODIMENTS
  • crank-shaft 20 is for use in a radial cylinder hydraulic motor, for example as shown in FIG. 4, and is mounted in at least two races of roller bearings 21, and an eccentric 22 is located between the bearing races.
  • the eccentric 22 comprises a circular annulus 23 whose outer face is slidingly engaged bycon-rod slippers (34 in FIG. 4) and which is carried at the outer ends of opposed pistons 24, 25 which are urgedoutwardly into contact with the annulus 23 by positioning springs 26, and the pistons are slidable in cylindrical recesses 27, 28 formed in body part 29 of the shaft 20.
  • the shaft section as shown in FIG. 2, is formed with flat side faces 30 and side pads 31 are keyed to the annulus 23 by keys 32.
  • the pads 31 are in sliding contact with the faces 30 and may be hydrostatically balanced, for example by means of recesses 33 supplied with high-pressure fluid through ducts (not shown) which are formed in the pads and are fed from bores 34C in the con-rod slippers 34B (FIG. 4).
  • the arcuate outer faces of the pistons 24, 25 are (optionally) formed with tongues 35 which enter a locating groove 36 in the inner face of the annulus 23.
  • hydraulic fluid is fed to the recesses 27, 28 from ducts 37, 38, respectively.
  • the ducts 37, 38 are formed in part 39 of the body of the hydraulic motor, and feed into channels 40, 41 which open into bores 42, 43 in the shaft 20 to feed to the recesses 27, 28.
  • the channels 40, 41 may be sealed against leakage by rings 44 and the whole assembly of channels, rings and casing comprises, in effect, a slip-ring assembly 45.
  • This assembly is at one end of the shaft 20 as shown in FIGS. 1 and 3, but may alternatively be at some other convenient position in the motor.
  • the swept volume can be varied by varying the throw of the eccentric 22 which determines the stroke of the reciprocating pistons 34 (FIG. 4).
  • the eccentric throw is varied by shifting the annulus 23 and this is effected by feeding differential fluid pressures to the recesses 27, 28 and so moving the pistons 24, 25 whichcarry theannulus.
  • FIG. 3 shows the position when high-pressure fluid is fed through duct 38 to piston 25, and low-pressure fluid is applied to piston 24.
  • the annulus 23 abuts against the shaft body part '29 and is held concentric with the shaft 20 to produce a zero-stroke or neutral drive effect which permits freewheeling of the shaft 20.
  • a spacer 46 shown in broken lines in FIGS. 1 and 2, may be provided to limit the inward movement of piston 24 and so provide for a minimumstroke, as opposed to a zero-stroke, position of the eccentric.
  • a similar spacer could be provided in recess 28 to limit the movement of piston and so reduce the maximum stroke.
  • the hydraulic fluid supply to ducts 37, 38 may be derived from the pump which drives the motor, or a separate auxiliary pump may be provided for this purpose.
  • the sizes of the pistons 24, 25 are determined by the pressure of the hydraulic supply available and must, of course, be sufficient to balance the driving force applied to the annulus 23. It will be noted that the diameter of piston 25 is slightly larger than that of piston 24. It has been found that, in low speed hydraulic motors of the present type, the shift of the annulus 23 requires the provision of two pistons, one (24) to increase .the eccentricity while the shaft is turning slowly or is stationary, and the other (25) to reduce the eccentricity. The hydraulic forces on the annulus which are to be overcome by these pistons vary during rotation of the crankshaft 20. The highest force to be overcome by piston 24 occurs when the annulus 23 is being moved from the concentric (free-wheel) position and, as the eccentricity increases, this opposing force decreases.
  • Piston 25 is required to decrease the eccentricity at all shaft speeds, and the maximum force required occurs when the annulus is being moved from the maximum eccentricity position; as the eccentricity decreases, so does this opposing force.
  • the hydraulic forces (and any centrifugal forces) on the eccentric act to increase its stroke and, at high speeds, only piston 25 would be required to move the annulus.
  • piston 24 may be necessary for moving the annulus to a position of greater eccentricity, in certain angular positions of the output shaft.
  • piston 24 could conceivably be performed by a spring powerful enough to overcome the force, and this would result in an uneconomically and unsuitably large form of eccentric (23).
  • the provision of two pistons also has the advantage of improving response to a servo control ina motor having an infinitely variable eccentricity.
  • the five radial cylinders 47 are fed through a pintle (distributor) valve 48 which directs hydraulic fluid to supply-and-return conduits 49.
  • Pistons 34 in the cylinders 47 drive the eccentric through con-rods 34A formed with slippers 348 which are in sliding engagement with the annulus 23 and are hydrostatically balanced through bores 34C.
  • the motor incorporates a crankshaft 20 as shown in FIGS. 1 to 3 but, as shown in FIG. 4 the channels 40, 4] are fed by ducts 50, 51 which are connected through a two-position control valve 52 to high-pressure supply 53 and to drain 54, respectively.
  • the valve 52 is located externally of the motor casing.
  • the control valve may be mounted on the motor casing or may be mounted remotely, and one valve may control more than one hydraulic motor.
  • one or more valves may be provided at the drivers controls in a vehicle having hydraulic wheel motors.
  • crank-shaft 20 shown in.FIG. 5 is basically similar to that described in FIGS. 1 to 3, but the FIG. 5 arrangement provides for infinite variation of the stroke, between predetermined limits.
  • a servo control system is provided.
  • valve spool 55 is housed in a bore 56 in valve body 57.
  • the spool 55 is urged to a central position by springs 58 and is formed with four lands which define chambers A, B, C, D, and E.
  • high-pressure fluid is supplied from one of the two motor-supply lines 59, through a shuttle valve 60 which selects the higher of the two line pressures.
  • the higher pressure is then fed through a first restriction 61 to a conduit 52 which pressurises chamber E and extends, through slip-ring assembly 45, to relief valve 63.
  • Relief valve 63 is loaded by a spring 64 whose compression depends on the degree of eccentricity of the annulus 23.
  • the high pressure fluid from shuttle valve 60 also passes through a second restriction 65 to a manually-operable control valve 66 having a drain outlet 67, and through a further conduit 68 to pressurise chamber A.
  • fluid pressures influenced by the valves 63 and 66 act in opposition on the valve spool 55.
  • High pressure fluid from shuttle valve 60 also passes to the bore 56 through a conduit 69 to be fed selectively to the conduits 42, 43 and thus to piston 24 or piston 25, depending on the position of valve spool 55.
  • the system is in a state of balance, with the lands on spool valve 55 closing the conduits 42 and 43; chamber C is also closed, and chambers B and D are open to drain (into the motor crank case) through conduit 70.
  • the valve spool 55 is displaced, for example by increase in fluid pressure from conduit 68 due to a change in the setting of control valve 66 or, alternatively, by fluctuating external forces on the annulus 23, high pressure fluid is fed from chamber C to the appropriate conduit to move piston 24 or 25.
  • the compression of spring 64 is altered to change the pressure in chamber A and the spool 55 gradually returns to its mid position.
  • Restrictions 71 may also be provided to act as dash-pots and damp the movements of spool 55.
  • a piston rod 72 carries the annulus 23 and extends through aligned bores 73, 74 in composite body part 29 of the shaft 20.
  • a piston member 75 secured to the rod 72 is movable within chamber 76 in the shaft body part, under the action of fluid pressures fed to the upper and lower compartments of the chamber, to vary the eccentricity of the annulus 23.
  • the upper length 72A of the piston rod has a diameter slightly larger than that of the lower length 72B, so that the effective area of the upper face of piston member 75 is less than that of the lower face.
  • the piston member 75 is formed with parts 77 which co-operate with recesses 78 to producea dashpot effect.
  • the annulus 23 is formed with recesses 80, 81 which receive complementary projections 82, 83 formed on the crowns of the opposed pistons 24 and 25.
  • the annulus is formed with inner flat faces 84 which directly engage the flat faces on the shaft body part 29 and thus eliminate the necessity for supplementary pads (31), as is also the case in FIGS. 5 and 6.
  • FIG. 8 shows a modification of the FIG. 7 construction, in which the opposed pistons 24, 25 are arranged around circular projections 90, 91 formed on the shaft body part 29 and the eccentricity of the annulus is varied by pressurising chambers 92, 93 through ducts 94, 95 which extend from bores such as 42, 43.
  • FIG. 9 shows an embodiment of the invention as applied to a radial-cylinder hydraulic motor of the type having piston-sleeves, e.g., as shown in British Pat. Specification No. 886,923.
  • a pentagon 100 is interposed between the eccentric annulus 23, and five piston-sleeves 101 bear against flat outer faces 102 of the pentagon.
  • the annulus 23 is rotated inside the orbiting pentagon 100 and the eccentricity of the annulus is controlled as in FIG. 8.
  • FIG. 9 shows an embodiment of the invention as applied to a radial-cylinder hydraulic motor of the type having piston-sleeves, e.g., as shown in British Pat. Specification No. 886,923.
  • a pentagon 100 is interposed between the eccentric annulus 23, and five piston-sleeves 101 bear against flat outer faces 102 of the pentagon.
  • the annulus 23 is rotated inside the orbiting pentagon 100 and the eccentricity of the annulus is controlled as in FIG. 8.
  • fluid pressure supply ducts 103 extend axially and then laterally through the shaft body part 29 and thence through the annulus and, through ducts 104 in the pentagon 100, into successive piston-sleeves 101 which are continuously urged inwardly by compression springs 105 and are in sealing engagement with the faces 102.
  • FIG. 10 shows a crank-shaft 20 for use in a rotarycasing motor such as a wheel motor.
  • the construction is similar to that of FIGS. 1 to 3 but, since the shaft 20 is stationary, the layout can be simplified and fluid can be fed directly to and through axial bores 130, 131 to the opposed pistons 24, 25. In the case. conversion of an existing motor would only require replacement of the crank-shaft and the provision of appropriate feeds to bores 130 and 131; the aforementioned part 39 (FIGS. 1 to 4) is not required.
  • FIG. 11 shows an alternative form of stationary or rotary crank-shaft having an eccentric whose throw is infinitely variable, between limits.
  • a servovalve device 140 which is similar to 55 in FIG. 5, is
  • the servo-valve devices have been described above as being hydraulically controlled but the servo-valves can be operated by, for example, mechanical means, and it is also envisaged that the eccentric shift might be effected by mechanical or electrical means rather than hydraulically.
  • the servo-valves may also be controlled by signals from devices sensing fluid pressure, fluid flow rate, torque, or speed, to provide automatic control of a particular function.
  • a radial cylinder hydraulic motor comprising a casing, a drive shaft journalled in said casing; an eccentric within said casing and extending about said drive shaft; a drive from said shaft to said eccentric to drive said eccentric; said drive shaft having oppositely facing cylindrical recesses therein facing said ecentric; said casing having a series of radial cylinders therein opening towards said eccentric and a drive piston in each radial cylinder to rotate said eccentric and thus said shaft, opposed control pistons in said cylindrical recesses having engagement with said eccentric; fluid pressure passageways to said cylindrical recesses; and valve means to admit fluid under pressure to said passageways and cylindrical recesses at variable pressures to vary the throw of said eccentric and thus the displacement of the motor, said control pistons and cylindrical recesses having different diameters, the control piston moving the eccentric towards the shaft axis to decrease the eccentricity being of smaller diameter than the control piston which moves the eccentric away from the shaft axis to increase the throw of the eccentric.
  • control pistons are effective to move the eccentric between drive and neutral positions and past a neutral position to a drive position, to enable the motor to reversely operate without altering the direction of supply fluid flow.
  • valve means to admit fluid pressure to said passageways comprises a servo-control system providing infinte variation of the throw of said eccentric between zero and a maximum.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Hydraulic Motors (AREA)
  • Reciprocating Pumps (AREA)
  • Fluid-Pressure Circuits (AREA)
US00221366A 1971-01-29 1972-01-27 Hydraulic motors and the like Expired - Lifetime US3828400A (en)

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GB353271A GB1385702A (en) 1971-01-29 1971-01-29 Hydraulic motors and the like

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AU (1) AU474577B2 (it)
DE (2) DE2265774C2 (it)
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IT (1) IT946911B (it)

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3908517A (en) * 1972-05-26 1975-09-30 Twin Disc Inc Hydrostatic engine control
US4051765A (en) * 1974-07-23 1977-10-04 Nisshin Sangyo Co., Ltd. Electric-hydraulic pulse motor having an improved rotary guide valve means
US4195553A (en) * 1978-05-16 1980-04-01 D. Duesterloh GmbH Fluid-displacement radial piston machine
US4237774A (en) * 1979-07-16 1980-12-09 Caterpillar Tractor Co. Displacement control valving for a radial piston device
US4320692A (en) * 1979-04-27 1982-03-23 Kayaba Kogyo Kabushiki Kaisha Radial cylinder hydraulic motor
US4365939A (en) * 1979-07-06 1982-12-28 Lucas Industries Limited Fuel injection pumping apparatus
US4543876A (en) * 1983-01-27 1985-10-01 Linde Aktiengesellschaft Axial piston machine having adjustable hydrostatically supported swashplate
US4548124A (en) * 1984-02-23 1985-10-22 Riva Calzoni S.P.A. Radial piston hydraulic motor with variable eccentricity
US4781104A (en) * 1986-02-24 1988-11-01 Shimadzu Corporation Rotary fluid energy translation device
US5054371A (en) * 1986-09-15 1991-10-08 Swinney Louis E Radial pump/motor
WO1998030807A1 (en) * 1997-01-10 1998-07-16 Brackett Douglas C On-the-fly, real-time controlled variable stroke crankshaft
US6030185A (en) * 1996-07-11 2000-02-29 Itt Manufacturing Enterprises Inc. Radial piston pump
EP2584197A1 (fr) * 2011-10-21 2013-04-24 Hydr'am Pompe hydraulique radiale a excentricite et debit variables
CN113339220A (zh) * 2021-07-06 2021-09-03 翁颇颖 一种扭矩无级变量调节的偏心轮组件及星型液压泵

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2448469C2 (de) * 1974-10-11 1986-05-15 Theodore Dipl.-Ing. 4030 Ratingen Sartoros Regelbare doppeltwirkende hydraulische Flügelzellenmaschine
DE2654526C3 (de) * 1976-12-02 1982-09-30 G. Düsterloh GmbH, 4322 Sprockhövel Hydrostatische Radialkolbenmaschine
DE2720306C2 (de) * 1977-05-06 1986-02-27 Robert Bosch Gmbh, 7000 Stuttgart Verdrängermaschine
JPS59124691A (ja) * 1982-12-29 1984-07-18 川崎重工業株式会社 液圧係船機制御装置
US4474104A (en) * 1983-04-11 1984-10-02 Double A Products Co. Control system for variable displacement pumps and motors
DE3313974A1 (de) * 1983-04-18 1984-10-25 Paul Pleiger Maschinenfabrik, 5810 Witten Verfahren und vorrichtung zum steuern von hydromotoren
DE3440543A1 (de) * 1984-11-07 1986-05-22 G. Düsterloh GmbH, 4322 Sprockhövel Fluidische radialkolbenmaschine
US4710106A (en) * 1984-11-26 1987-12-01 Nippondenso Co., Ltd. Volume controlling device for variable volume pump
NL8500402A (nl) * 1985-02-13 1986-09-01 Schelde Nl Aandrijving van verbruikers aan boord van een schip.
DE3513736A1 (de) * 1985-04-17 1986-10-30 G. Düsterloh GmbH, 4322 Sprockhövel Hydrostatische radialkolbenmaschine
DE3518652A1 (de) * 1985-05-23 1986-11-27 Paul Pleiger Maschinenfabrik GmbH & Co KG, 5810 Witten Drehdurchfuehrung fuer einen radialkolbenmotor
DE3818105A1 (de) * 1988-05-27 1989-12-07 Pleiger Maschf Paul Vorrichtung zum verstellen des schluckvolumens eines radialkolbenmotors
DE3900888A1 (de) * 1989-01-13 1990-07-26 Rexroth Mannesmann Gmbh Radialkolbenmaschine
IT1271634B (it) * 1994-04-29 1997-06-04 Riva Calzoni Spa Motore idraulico a cilindri radiali a cilindrata variabile mediante attuatori separati e relative valvole di comando

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1149728A (en) * 1912-08-14 1915-08-10 Esteban Ciarlo Mechanical movement.
US2404175A (en) * 1942-06-25 1946-07-16 Vickers Armstrongs Ltd Hydraulic pump of the radial cylinder type
US2836120A (en) * 1954-09-14 1958-05-27 Navarro Miguel Variable capacity pump
US3036557A (en) * 1959-06-04 1962-05-29 Kimsey Eric George Hydraulic motors and pumps
US3067728A (en) * 1958-10-31 1962-12-11 Bordini Giovanni Method and apparatus for motion conversion and transmission
US3255707A (en) * 1963-12-02 1966-06-14 Haviland H Platt Hydraulic pumps and motors of the displacement type
US3354786A (en) * 1960-12-21 1967-11-28 Chamberlain Ind Ltd Hydraulic motors
US3732037A (en) * 1971-05-27 1973-05-08 F Carlson Pump displacement control
US3737014A (en) * 1971-09-27 1973-06-05 W Dalrymple Coupling assembly

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR945332A (fr) * 1947-04-01 1949-05-02 Pompe hydraulique à volume variable
DE1188948B (de) * 1960-07-16 1965-03-11 Metallwerk Glockerau G M B H Arbeitsfluessigkeitsmengen-Regeleinrichtung fuer hydrostatische Pumpen und Motoren
US3067963A (en) * 1961-02-03 1962-12-11 Fletcher N Suggs Toilet tissue roll holder
US3179061A (en) * 1962-02-23 1965-04-20 Weatherhead Co Variable displacement pump control
GB1085232A (en) * 1963-06-25 1967-09-27 Chamberlain Ind Ltd Improvements in or relating to hydraulic motors
DE1929645C3 (de) * 1969-06-09 1975-03-13 Mannesmann-Meer Ag, 4050 Moenchengladbach Regelvorrichtung zum Konstanthalten des Verdrängungsvolumens von Flüssigkeitspumpen oder -motoren

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1149728A (en) * 1912-08-14 1915-08-10 Esteban Ciarlo Mechanical movement.
US2404175A (en) * 1942-06-25 1946-07-16 Vickers Armstrongs Ltd Hydraulic pump of the radial cylinder type
US2836120A (en) * 1954-09-14 1958-05-27 Navarro Miguel Variable capacity pump
US3067728A (en) * 1958-10-31 1962-12-11 Bordini Giovanni Method and apparatus for motion conversion and transmission
US3036557A (en) * 1959-06-04 1962-05-29 Kimsey Eric George Hydraulic motors and pumps
US3354786A (en) * 1960-12-21 1967-11-28 Chamberlain Ind Ltd Hydraulic motors
US3255707A (en) * 1963-12-02 1966-06-14 Haviland H Platt Hydraulic pumps and motors of the displacement type
US3732037A (en) * 1971-05-27 1973-05-08 F Carlson Pump displacement control
US3737014A (en) * 1971-09-27 1973-06-05 W Dalrymple Coupling assembly

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3908517A (en) * 1972-05-26 1975-09-30 Twin Disc Inc Hydrostatic engine control
US4051765A (en) * 1974-07-23 1977-10-04 Nisshin Sangyo Co., Ltd. Electric-hydraulic pulse motor having an improved rotary guide valve means
US4195553A (en) * 1978-05-16 1980-04-01 D. Duesterloh GmbH Fluid-displacement radial piston machine
US4320692A (en) * 1979-04-27 1982-03-23 Kayaba Kogyo Kabushiki Kaisha Radial cylinder hydraulic motor
US4365939A (en) * 1979-07-06 1982-12-28 Lucas Industries Limited Fuel injection pumping apparatus
US4237774A (en) * 1979-07-16 1980-12-09 Caterpillar Tractor Co. Displacement control valving for a radial piston device
US4543876A (en) * 1983-01-27 1985-10-01 Linde Aktiengesellschaft Axial piston machine having adjustable hydrostatically supported swashplate
US4548124A (en) * 1984-02-23 1985-10-22 Riva Calzoni S.P.A. Radial piston hydraulic motor with variable eccentricity
US4781104A (en) * 1986-02-24 1988-11-01 Shimadzu Corporation Rotary fluid energy translation device
US5054371A (en) * 1986-09-15 1991-10-08 Swinney Louis E Radial pump/motor
US6030185A (en) * 1996-07-11 2000-02-29 Itt Manufacturing Enterprises Inc. Radial piston pump
WO1998030807A1 (en) * 1997-01-10 1998-07-16 Brackett Douglas C On-the-fly, real-time controlled variable stroke crankshaft
EP2584197A1 (fr) * 2011-10-21 2013-04-24 Hydr'am Pompe hydraulique radiale a excentricite et debit variables
FR2981703A1 (fr) * 2011-10-21 2013-04-26 Hydr Am Pompe hydraulique radiale a excentricite et debit variables
US9194380B2 (en) 2011-10-21 2015-11-24 Hydr'am Radial hydraulic pump with a variable eccentricity and delivery
CN113339220A (zh) * 2021-07-06 2021-09-03 翁颇颖 一种扭矩无级变量调节的偏心轮组件及星型液压泵
CN113339220B (zh) * 2021-07-06 2023-09-05 翁颇颖 一种扭矩无级变量调节的偏心轮组件及星型液压泵

Also Published As

Publication number Publication date
IT946911B (it) 1973-05-21
DE2203054A1 (de) 1972-08-24
JPS591116Y2 (ja) 1984-01-12
GB1385702A (en) 1975-02-26
AU474577B2 (en) 1976-07-29
DE2265774C2 (it) 1988-04-14
JPS55135168U (it) 1980-09-25
DE2203054C2 (de) 1983-10-27
AU3816972A (en) 1973-07-26

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