US3808951A - Hydraulic motors - Google Patents

Hydraulic motors Download PDF

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Publication number
US3808951A
US3808951A US00230013A US23001372A US3808951A US 3808951 A US3808951 A US 3808951A US 00230013 A US00230013 A US 00230013A US 23001372 A US23001372 A US 23001372A US 3808951 A US3808951 A US 3808951A
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United States
Prior art keywords
orifices
groove
cams
conduit
group
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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US00230013A
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English (en)
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L Martin
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Poclain Hydraulics France SA
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Individual
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Assigned to POCLAIN HYDRAULICS, A FRANCE FIRM reassignment POCLAIN HYDRAULICS, A FRANCE FIRM ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: POCLAIN
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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
    • F03C1/045—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
    • 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
    • F03C1/0409—Cams

Definitions

  • ABSTRACT This invention relates to a hydraulic motor constituted by a cylinder block mounted to rotate in a support, by two groups of cams integral with said support, by rollers integral in translation with pistons contained in the cylinders of the cylinder block and in abutment on said cams, and by a valve coaxial with the axis of the cylinder block and provided with a slide for selecting the running conditions of the motor, with three positions, each cylinder comprises a pipe connecting it successively to a plurality of orifices disposed in two groups, which each correspond to a group of cams, and the orifices of the same group are regularly distributed on the valve, whilst the orifices of the group of orifices corresponding to the first group of cams comprise first and second orifices, which are alternately placed in communication, the first orifices with a first conduit connected to a source of
  • the present invention relates to a method for obtaining particular running conditions of a hydraulic motor, and motor for carrying out the method.
  • the expression hydraulic motor means the different hydraulic machines which, connected to a hydraulic circuit and provided with a shaft connected to a rotor, function effectively as motor, when the pressure of the fluid is higher in the admission conduit than in the delivery conduit, and when the shaft is then driven by the rotor, and which operate as pump, when on the contrary the pressure of the fluid is higher in the delivery conduit than in the admission conduit, and when the shaft then drives the rotor.
  • the single expression motor for designating the abovementioned machines.
  • the cams of said motor have been divided into at least two groups, and, with the aid of a selection slide valve, either the cylinders disposed opposite the first group of cams or those disposed opposite the second group, or the cylinders disposed opposite the two groups, are fed in parallel. If the strokes of the two groups of cams are equal, two possible speeds of rotation are obtained; if they are unequal, the number of possible speeds of rotation is three.
  • a process is therefore applied for obtaining particular running conditions of a hydraulic motor comprising two groups of cams, according to which, in order toobtain a first running, the cylinders disposed opposite the cams of at least one of the two groups of cams are fed with fluid, whilst, when the cylinders disposed opposite the cams of the two groups of cams are fed with fluid, this latter feed is effected by connecting said cylinders in parallel.
  • the cylinders disposed opposite the cams of the two groups of cams are fed with fluid by effecting the connection of the feeds of the cylinders disposed opposite the cams of a first group of the two groups of cams in opposition with the feeds of the cylinders disposed opposite the cams of the second group of cams.
  • the invention also, and more particularly, has for its object a hydraulic motor for carrying out the preceding method and constituted by a cylinder-block mounted to rotate in a support, by two groups of cams integral with said support, by rollers integral in translation with pistons contained in the cylinders of the cylinder block and in abutment on said cams and by a valve coaxial with the axis of the cylinder block and provided with a slide for selecting the running conditions of the motor with three positions.
  • Each cylinder comprises-a pipe connecting it successivelyto a plurality of orifices disposed in two groups, each of which corresponds to a group of cams, the orifices of the same group being regularly distributed on the valve.
  • the orifices of the group of orifices corresponding to the first group of cams comprise first and second orifices, which are alternately placed in communication, the first orifices with a first conduit connected to a source of pressurised fluid or to a discharge tank, the second orifices, which'follow the-first orifices, with a second conduit connected to the discharge tank, or to the source of pressurised fluid, respectively.
  • the orifices of the group of orifices corresponding to the second group of cams comprise third and fourth orifices, which are alternately placed in communication, respectively, and sele'ctively by means of the selection slide, the third orifices with the first conduit or with the second conduit, or with the fourth orifices, whichfollow said third orifices and, the fourth orifices with the second conduit, or with the first conduit, or with said third orifices.
  • the selection slide is cylindrical, coaxial with the valve and capable of being displaced in translation parallel to its axis opposite five grooves made in said valve.
  • Said grooves are in permanent communication, the first with the fifth, the second with the first conduit, and the fourth with the second conduit, and are in selective communication, in the first position of the slide, the first groove with the second, and the third with the fourth, in'the second position of the slide, the second groove with the third, and the fourth with the fifth, and, finally, in 'the third position of the slide, the third groove with the fourth and the fifth groove, and the second groove being isolated from theother grooves.
  • the first groove is advantageously placed in permanent communication with'the fifth groove by means of a complementary pipe arranged in the valve.
  • the sections of the different pistons contained in the cylinders are identical, whilst the first stroke of axial clearance of a piston, whose roller is in abutment on the cam of the first group of cams and is displaced between a summit and a notch of said cam, and the second stroke of axial clearance of a piston, whose roller has been displaced between the summit and the notch of a cam of the second group of cams, have unequal values.
  • the two groups of cams preferably contain the same transverse plane perpendicular to the axis of rotation of the cylinder block, whilst the cams of the two groups are continuously connected and follow one another, alternately, a cam of the first group, then a cam of the second group.
  • the angle of rotation which enables the zone of abutment of the roller of a pistonto be displaced froma summit or a notch of a camof the first group of cams to the following summit or notch of the same cam of said first group
  • the angle of rotation which enables the zone of abutment of the roller of a piston to be displaced from a summit or a notch of a cam of the second group of cams to the following summit or notch of the same cam of said second group have unequal values.
  • FIGS. 1, 2 and 3 are diagrams relative to the three possible running operations of a motor according to the invention.
  • FIG. 4 is an axial section of a motor according to the invention.
  • FIG. 5 is a part transverse section along V-V of FIG. 4 through the motor shown in FIG. 4.
  • FIGS. '6, 7, 8 and 9 are transverse sections along VI- VI, VII-VII, VIII-VIII and lXlX respectively, of FIG. 4, through the valve and slide of the valve of the motor shown in FIG. 4.
  • the method-according to the invention firstly consists in making a hydraulic motor inknown manner, giving it two groups of cams, of generally different strokes, which are generally referenced by C and C C being greater than C and each group having the same number of cams as the other group.
  • the following operation consisted in the production of separate feeds for the two imaginary motors constituted by the cylinders momentarily disposed opposite the cams, of the first group of cams for the first motor, the second group of cams for the second motor.
  • the abovementioned imaginary motors which correspond to groups ofcylinders of the same real motor, in fact possess only one single rotor. This arrangement will be specified later.
  • one of the three running conditions described hereinbelow may be chosen.
  • the imaginary motors l and 2 have their respective inlets 3 and 4 connected in parallel to a first conduit 5, itself connected to a source of pressurised fluid in direction of arrow F, or further are both connected in parallel to a second conduit 6,
  • the running, illustrated in FIG. 2 is the particular running which had never been obtained before. It enables, with cams of strokes C close to C a very high speed of rotation of the motor to be obtained, said cams being furthermore of any type and not being particularly difficult to manufacture with respect to the conventional cams.
  • a third running of the motor may easily be obtained by effecting the connections of FIG. 3.
  • the inlet and delivery conduits 4 and 8 of the motor 2 are connected and consequently only motor 1 is in fact fed, with the feed flow coming from the source of pressurised fluid.
  • the conduits 4 and 8 are connected to a complementary conduit 9, which is itself connected to conduit 5, but which in fact plays no active role in the present connection.
  • the speed of rotation of the motor obtained in the course of this running is inversely proportional to the stroke C and has a value which is intermediary between the values of the speeds obtained during the two running conditions described hereinabove.
  • the conduit 7 nowfconstitutes one and the same conduit with the second conduit connected either to the discharge tank or to the source of pressurised fluid.
  • the invention proposes the type of motor described hereinafter with reference to FIGS. 4 to 9.
  • the motor shown is constituted by a cylinder block 10, which is mounted to rotate in a casing 11 with which cams I2 and 13 of two different types are integral.
  • the cams l2 and 13 are disposed in the same transverse plane in order to cooperate with the rollers 14 which are integral in translation with the pistons 15 mounted to slide in cylinders 16, arranged in the cylinder block 10 and disposed radially in said cylinder block.
  • a cam 13 with large stroke C follows a cam 12 with small stroke C being continuously connected to the section of the two cams 12 disposed on either side of said cam 13.
  • the motor shown comprises three cams l2 and three cams 13.
  • a cylindrical valve 17 is integral .in rotation with the casing 11, except for a small clearance for adjustment.
  • the cylinder block 10 is thus mounted to rotate with respect to this valve.
  • Orifices are made on the outer periphery 17a of the valve 17, and are so disposed that they are in alternate communication with the cylinders 16 by conduits 18 connecting said cylinders to the inner periphery 10a of the cylinder .block 10.
  • orifices correspond in twos to a cam 12 or 13 and are in fact of four distinct types: orifices l9 and 20, which correspond to cams 13, and orifices 21 and 22 which correspond to earns 12.
  • a selection slide 23 which is cylindrical and coaxial with the valve 17, is mounted to slide axially in said valve.
  • the slide 23 is held in its central position by a spring 24, interposed between two discs 25 connected to said slide, and may be displaced on either side of this central position, in order to be disposed in two other positions, by admission of pressurised fluid in one of the two chambers 26 or 27 located at the ends of the slide by a conduit 28 or 29, and placed in communication with a discharge tank of the other chamber 27 or 26, by means of the other conduit 29 or 28.
  • This device for adjusting the position of the slide is therefore of hydraulic nature and may be remotely controlled.
  • the slide 23 comprises three shoulders 30, 31, 32 which are displaced opposite five grooves 33, 34, 35, 36 and 37, made in the valve 17.
  • the slide 23 In its first position, the slide 23 is pushed entirely to the right, the pressurised control fluid being present in the chamber 26.
  • the chambers35 and 36 communicate together in the same way as chambers 33 and 34, the shoulders 31 and being in positions permitting these communications.
  • the second position of the slide In the second position of the slide, the latter is on the contrary pushed completely towards the left, the pressurised control fluid then being contained in the chamber 27.
  • the various shoulders then occupy such positions that the grooves 34 and 35 communicate together, similarly to the grooves 36 and 37.
  • the shoulders 30 and 31 isolate the groove 34 from the grooves 33 and 35, whilst grooves 35, 36 and 37 are placed in communication.
  • the groove 34 is in permanent communication with the conduit 5 by a conduit 38 made in the valve 17
  • the groove 36 is itself in permanent communication with the conduit 6 by a conduit 39 made in the said valve 17, andfinally a conduit 40 also arranged in the valve 17, permanently connects the end grooves 33 and 37.
  • FIGS. 6 to 9 show the communications ensured inside the valve 17 itself.
  • conduits 38 connect the groove 34 to the different orifices 20 and to the conduit 5, the conduit 5 being in fact divided into two in order to permit a better flow of the inlet or delivery flow of the fluid to be conveyed.
  • conduits 39 are shown and connect the various orifices 19 to the groove 36 (and to conduit 6), the conduit 6 also being divided in two for the same reasons as conduit 5.
  • orifices 21 and 22 are placed in communication, respectively, with corresponding grooves 35 and 33, by conduits 41 and 42.
  • the sections of the cams l2 and 13 are defined as being homokinetic. This signifies the fact that, when the cylinder block rotates at a given speed of rotation, the sum of the linear speeds of the pistons disposed opposite the cams of the same group is substantially constant, this having for its advantage to procure the constancy of the inlet and delivery flows of the fluid contained in the cylinders relative to said pistons.
  • the motor which has been described is however easy to manufacture.
  • the earns 12 and 13 are commonplace and do not have to have very small strokes for the difference between the extreme operational speeds of the motor to be obtained. In fact, these speeds are associated only with the ratio (C l C (C, C which may be very large, although C and C keep usual values.
  • cams l2 and 13 could be disposed, not in the same transverse plane asin the example shown, but in two distinct transverse planes, one plane containing the cams l2 and the second plane containing the cams 13.
  • the motors according to the invention may be used in many ways, such as, inter alia, the propulsion of public works machines at a low speed and a high speed.
  • Hydraulic motor comprising a cylinder block mounted to rotate in a support, two groups of cams integral with said support, each group of cams being formed to produce a different piston displacement, rollers integral in translation with pistons contained in cylinders formed in the cylinder block and in abutment on said earns, a valve coaxial with the axis of the cylinder block, said valve being provided with a slide for selecting the running conditions of the motor, each cylinder having a conduit associated therewith a conduit connecting it successively to each of a plurality of orifices disposed in two groups, each'of which correspond to a different group of said cams, with the orifices of the same group being regularly distributed on the valve, the orifices of the group of orifices corresponding to the first group of cams comprising first and second orition with a first conduit connected to a source of pressurized fluid and a second conduit connected to a discharge tank respectively, and the orifices of the group of orifices corresponding to the second group of

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
  • Reciprocating Pumps (AREA)
US00230013A 1971-03-02 1972-02-28 Hydraulic motors Expired - Lifetime US3808951A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR7107153A FR2127268A5 (enrdf_load_stackoverflow) 1971-03-02 1971-03-02

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US3808951A true US3808951A (en) 1974-05-07

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US00230013A Expired - Lifetime US3808951A (en) 1971-03-02 1972-02-28 Hydraulic motors

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US (1) US3808951A (enrdf_load_stackoverflow)
JP (1) JPS5738788B1 (enrdf_load_stackoverflow)
BE (1) BE779698A (enrdf_load_stackoverflow)
DE (1) DE2209152A1 (enrdf_load_stackoverflow)
ES (1) ES400345A1 (enrdf_load_stackoverflow)
FR (1) FR2127268A5 (enrdf_load_stackoverflow)
GB (1) GB1384451A (enrdf_load_stackoverflow)
IT (1) IT952886B (enrdf_load_stackoverflow)

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4157056A (en) * 1976-09-21 1979-06-05 Poclain Hydraulics Multi-cylinder hydraulic mechanism
US4318336A (en) * 1980-04-24 1982-03-09 Rudolf Bock Hydraulic motor
US4346645A (en) * 1978-11-04 1982-08-31 G. L. Rexroth Gmbh Hydraulic axial piston engine
US4605359A (en) * 1984-02-28 1986-08-12 Nippondenso Co., Ltd. Radial plunger pump
US4898076A (en) * 1987-02-25 1990-02-06 Societe Anonyme: Poclain Hydraulics, B.P. Multiple cylinder-capacity pressurized fluid (motor or pump) mechanism
US5106347A (en) * 1988-11-08 1992-04-21 Nissan Motor Co., Ltd. Rotational speed differential responsive type torque transmitting assembly with variable orifice means
US5186094A (en) * 1991-06-25 1993-02-16 Poclain Hydraulics Pressurized fluid mechanism comprising at least two distinct operational cylinder capacities
US5281104A (en) * 1991-08-22 1994-01-25 Mercedes-Benz Ag Sequential displacement piston pump
US6114560A (en) * 1998-06-08 2000-09-05 Shin-Etsu Chem Co., Ltd. Method for preparing a short-chain polysulfide silane mixture
FR2844836A1 (fr) * 2002-09-24 2004-03-26 Linde Ag Machine volumetrique hydrostatique a debit volumetrique reglable en continu
US20060042459A1 (en) * 2002-10-02 2006-03-02 Felice Pecorari High efficiency hydraulic machine with radial cylinders
FR2881173A1 (fr) * 2005-01-27 2006-07-28 Ericab Sarl Machine tournante volumetrique
US10690109B2 (en) 2015-11-10 2020-06-23 Poclain Hydraulics Industrie Distribution device for a hydraulic machine and a hydraulic machine fitted with such a device
US20220389902A1 (en) * 2021-06-07 2022-12-08 Robert Bosch Gmbh Multi Piston Machine with at least Three Switchable Displacement Volumes
US20240044319A1 (en) * 2020-12-16 2024-02-08 Danfoss Power Solutions (Jiangsu) Co. Ltd. Hydrostatic radial piston unit
US20240328381A1 (en) * 2021-12-16 2024-10-03 Danfoss Power Solutions (Jiangsu) Co., Ltd. Brake mechanism for a radial piston unit

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2481755A1 (fr) * 1980-04-30 1981-11-06 Poclain Hydraulics Sa Moteur a fluide sous pression muni d'un dispositif de selection de sa vitesse de rotation
FR2526497B1 (fr) * 1982-05-10 1986-04-18 Mo N Proizv Machine hydraulique axiale a piston rotatif
AU566382B2 (en) * 1982-12-24 1987-10-15 Renold Plc Cam driven piston pump with variable capacity control
DE3706460A1 (de) * 1986-10-31 1988-09-08 Rexroth Mannesmann Gmbh Kolbenmaschine mit umschaltbarem hubraum
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.
DE19733911C1 (de) * 1997-08-05 1998-07-16 Mannesmann Rexroth Ltd Hydrostatische Maschine mit Gehäusespülung
DE19749906A1 (de) * 1997-11-12 1999-05-20 Halm Peter Radialkolben-Hydromotor
DE102010053977A1 (de) * 2010-12-09 2012-06-14 Rheinisch-Westfälische Technische Hochschule Aachen Steuerwelle eines pneumatischen Verdrängeraggregates

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2442125A (en) * 1944-02-02 1948-05-25 Gunning Maximiliaan Frederik Hydraulic motor and control therefor
US2562363A (en) * 1948-02-05 1951-07-31 Vickers Inc Compound fluid motor unit
US2650543A (en) * 1944-10-28 1953-09-01 Installation Et D App Soc D High-pressure radial piston pump for liquids
US3296937A (en) * 1965-05-28 1967-01-10 Poclain Sa Speed change device for an hydraulic motor
US3357312A (en) * 1964-08-13 1967-12-12 Inst Gornogo Dela Imeni Skochi Radial-piston hydraulic motor
US3369457A (en) * 1964-06-03 1968-02-20 Poclain Sa Hydraulic motor with speed change device
US3403599A (en) * 1965-10-08 1968-10-01 Poclain Sa Hydraulic motor change-speed system
US3593621A (en) * 1968-02-07 1971-07-20 Poclain Sa Hydraulic motor

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2442125A (en) * 1944-02-02 1948-05-25 Gunning Maximiliaan Frederik Hydraulic motor and control therefor
US2650543A (en) * 1944-10-28 1953-09-01 Installation Et D App Soc D High-pressure radial piston pump for liquids
US2562363A (en) * 1948-02-05 1951-07-31 Vickers Inc Compound fluid motor unit
US3369457A (en) * 1964-06-03 1968-02-20 Poclain Sa Hydraulic motor with speed change device
US3357312A (en) * 1964-08-13 1967-12-12 Inst Gornogo Dela Imeni Skochi Radial-piston hydraulic motor
US3296937A (en) * 1965-05-28 1967-01-10 Poclain Sa Speed change device for an hydraulic motor
US3403599A (en) * 1965-10-08 1968-10-01 Poclain Sa Hydraulic motor change-speed system
US3593621A (en) * 1968-02-07 1971-07-20 Poclain Sa Hydraulic motor

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4157056A (en) * 1976-09-21 1979-06-05 Poclain Hydraulics Multi-cylinder hydraulic mechanism
US4346645A (en) * 1978-11-04 1982-08-31 G. L. Rexroth Gmbh Hydraulic axial piston engine
US4318336A (en) * 1980-04-24 1982-03-09 Rudolf Bock Hydraulic motor
US4605359A (en) * 1984-02-28 1986-08-12 Nippondenso Co., Ltd. Radial plunger pump
US4898076A (en) * 1987-02-25 1990-02-06 Societe Anonyme: Poclain Hydraulics, B.P. Multiple cylinder-capacity pressurized fluid (motor or pump) mechanism
US5106347A (en) * 1988-11-08 1992-04-21 Nissan Motor Co., Ltd. Rotational speed differential responsive type torque transmitting assembly with variable orifice means
US5186094A (en) * 1991-06-25 1993-02-16 Poclain Hydraulics Pressurized fluid mechanism comprising at least two distinct operational cylinder capacities
US5281104A (en) * 1991-08-22 1994-01-25 Mercedes-Benz Ag Sequential displacement piston pump
US6114560A (en) * 1998-06-08 2000-09-05 Shin-Etsu Chem Co., Ltd. Method for preparing a short-chain polysulfide silane mixture
FR2844836A1 (fr) * 2002-09-24 2004-03-26 Linde Ag Machine volumetrique hydrostatique a debit volumetrique reglable en continu
US20060042459A1 (en) * 2002-10-02 2006-03-02 Felice Pecorari High efficiency hydraulic machine with radial cylinders
FR2881173A1 (fr) * 2005-01-27 2006-07-28 Ericab Sarl Machine tournante volumetrique
US10690109B2 (en) 2015-11-10 2020-06-23 Poclain Hydraulics Industrie Distribution device for a hydraulic machine and a hydraulic machine fitted with such a device
US20240044319A1 (en) * 2020-12-16 2024-02-08 Danfoss Power Solutions (Jiangsu) Co. Ltd. Hydrostatic radial piston unit
US20220389902A1 (en) * 2021-06-07 2022-12-08 Robert Bosch Gmbh Multi Piston Machine with at least Three Switchable Displacement Volumes
EP4102051A1 (en) * 2021-06-07 2022-12-14 Robert Bosch GmbH Multi piston machine with at least three switchable displacement volumes
EP4102052A1 (en) * 2021-06-07 2022-12-14 Robert Bosch GmbH Multi piston machine with at least three switchable displacement volumes
US12404832B2 (en) * 2021-06-07 2025-09-02 Robert Bosch Gmbh Multi piston machine with at least three switchable displacement volumes
US20240328381A1 (en) * 2021-12-16 2024-10-03 Danfoss Power Solutions (Jiangsu) Co., Ltd. Brake mechanism for a radial piston unit

Also Published As

Publication number Publication date
GB1384451A (en) 1975-02-19
DE2209152A1 (de) 1972-09-21
JPS5738788B1 (enrdf_load_stackoverflow) 1982-08-17
FR2127268A5 (enrdf_load_stackoverflow) 1972-10-13
BE779698A (fr) 1972-06-16
ES400345A1 (es) 1975-07-16
IT952886B (it) 1973-07-30

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AS Assignment

Owner name: POCLAIN HYDRAULICS, SOCIETE ANONYME, 60410 VERBERI

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:POCLAIN;REEL/FRAME:004596/0964

Effective date: 19860623