US3913455A - Radial-piston rotary hydrostatic machines - Google Patents

Radial-piston rotary hydrostatic machines Download PDF

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Publication number
US3913455A
US3913455A US435955A US43595574A US3913455A US 3913455 A US3913455 A US 3913455A US 435955 A US435955 A US 435955A US 43595574 A US43595574 A US 43595574A US 3913455 A US3913455 A US 3913455A
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United States
Prior art keywords
cylinders
leaf spring
piston
cylinder block
pistons
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Expired - Lifetime
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US435955A
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English (en)
Inventor
Paul Clifford Green
Keith Oswin Moore
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NEWAGE TRANSMISSIONS Ltd BARLOW ROAD COVENTRY CV2 2LD
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Newage Engineers Ltd
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Assigned to NEWAGE TRANSMISSIONS LIMITED, BARLOW ROAD COVENTRY CV2 2LD reassignment NEWAGE TRANSMISSIONS LIMITED, BARLOW ROAD COVENTRY CV2 2LD ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: NEWAGE ENGINEERS LIMITED
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Classifications

    • 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
    • F01B1/0603—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 the connection of the pistons with an element being at the outer ends of the cylinders
    • F01B1/061—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 the connection of the pistons with an element being at the outer ends of the cylinders with two or more series radial piston-cylinder units
    • F01B1/0613—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 the connection of the pistons with an element being at the outer ends of the cylinders with two or more series radial piston-cylinder units directly located side by side
    • 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
    • F01B1/0641—Details, component parts specially adapted for such machines
    • F01B1/0665—Disconnecting the pistons from the actuating or actuated cam
    • 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
    • F03C1/0438—Particularities relating to the distribution members to cylindrical distribution members

Definitions

  • ABSTRACT A hydrostatic motor or pump which comprises a cylinder block with two banks of radial cylinders surrounded by a relatively rotatable cam ring affording cam tracks which coact with follower rollers carried by radially-reciprocable pistons in the cylinders.
  • a circular leaf spring accommodated in a circumferential groove in the cylinder block marginally overlies the bodies of the pistons in the two banks being disposed between their follower rollers, and resiliently biasses the pistons radially inwardly to their innermost positions, the leaf spring acting on the pistons via interposed rollers or via radial pegs carried by the pistons.
  • a machine of this type which may be operated either as a hydrostatic motor or as a positive-displacement pump, has a cylinder block formed with one or more banks of radial cylinders in which piston assemblies reciprocate radially, the piston assemblies having cam followers, e.g. balls or rollers, which co-act with a circumferential cam profile formed on a cam ring which is co-axial with and rotatable relatively to the cylinder block.
  • cam followers e.g. balls or rollers
  • the cam ring may surround the cylinder block or vice versa, and either the cylinder block may be fixed and the cam ring rotatable about the axis of the cylinder block, or vice versa.
  • the inner ends of the cylinders are connected in the required sequence to a supply of pressurised hydraulic fluid and to a hydraulic return line, the resultant radial reciprocation of the pistons producing the required relative rotary drive between the cylinder block and the cam ring.
  • An object of the present invention is to provide a hydrostatic motor of the type referred to above with a simple means for preventing the cam followers of the piston assemblies from hitting their associated cam surface under such conditions.
  • Another object of the present invention is to provide arotary hydrostatic machine of the kind specified, with a radially-resilient circular spring, e.g. a leaf spring formed by a fiat spring strip curled lengthwise into circular form with its two end portions overlapping one another, which co-acts with the piston-and-follower assemblies of either one bank or two adjacent banks of the cylinders, and acts radially on each piston thereof to hold the piston resiliently in a radially-withdrawn position in which its follower is clear of the whole of the associated relatively-rotating cam profile.
  • a radially-resilient circular spring e.g. a leaf spring formed by a fiat spring strip curled lengthwise into circular form with its two end portions overlapping one another, which co-acts with the piston-and-follower assemblies of either one bank or two adjacent banks of the cylinders, and acts radially on each piston thereof to hold the piston resiliently in a radially-withdrawn position in which its follower is clear of the whole of the associated relatively-rot
  • the or each circular spring may be a leaf spring located in a circumferential groove formed in the exterior of the cylinder block and intersecting all the cylinders of at least one bank on one side of the cylinders.
  • one edge of the or each circular leaf spring will overlie a part of the circular body of each piston outside one end face of the cylindrical follower roller carried by the piston, so as to engage the piston radially with respect to the cylinder block, either directly or through the intermediary of a small roller or a radial peg or some other interposed member.
  • FIG. 1 is a diagrammatic side view of the cylinder block of a hydrostatic motor of the type specified;
  • FIG. 2 is a diagrammatic view of the cylinder block and surrounding cam ring of the motor, in section through the groove P in the cylinder block but showing only two cylinders of the block;
  • FIG. 3 is a view in axial section of a second embodiment of hydrostatic motor, the section line being indicated at III-III in FIG. 4;
  • FIG. 4 is a cross-section on the line IVIV of FIG. 3, showing the machine with its pistons retracted.
  • FIG. 5 is a fragmentary view showing the rotatable central pintle and porting arrangements of the motor.
  • FIGS. 1 and 2 shows schematically a hydrostatic motor which comprises a cam ring A formed with an internal endless circumferential cam profile Al and surrounding coaxially a cylinder block B formed with two banks each of six radial cylinders, l to 6 and 1', 2', etc.
  • the cam ring profile Al is shown purely diagrammatically in FIG. 2, no attempt having been made to illustrate its exact configuration.
  • the cylinder block B is formed with a circumferential groove P in which is located a circular leaf spring F, whose two ends F1 and F2 overlap one another to allow the resilient radial expansion and contractionbf the spring.
  • the groove P intersects the cylinders of the two adjacent banks on their adjacent sides as shown, to a radial depth insufficient to open into the inner ends of the cylinders when their pistons are at their radially-outermost positions at the ends of theiroutward strokes.
  • the piston C themselves carry cylindrical follower rollers D, each roller D' being journalled in apart-cylindrical bearing shell G whose end portions, backed by opposed skirt portions H of the piston, extend'around somewhat more than of the circumference of the respective roller D so that the roller is trapped'in' its journal shell and cannot escape radially from the piston.
  • each piston C is cut away at H1 on either side up to the corresponding end face of its rol-lerD; and each shell G is correspondingly cut away, to accommodate the overlapping edge portion of the circular leaf spring F, and a small roller E is trapped between the margin of the leaf spring F and the margin of the concave surface of the bearing shell G at the base of the cut-away side of the piston, so that the spring F canfact radially inwardly on each pistonC via the roller E to bias the piston radially inwardly and to tend to hold the piston resiliently in its innermost radial position, in which the follower roller D is clear of the path of the peaks of the cam profile A1 as the latter rotates relatively to'the cylinder block.
  • Conventional rotary valve arrangements are provided for connecting the inner ends of the cylinders cyclically, via passages R, to the fluid pressure inlet and return ports (not shown) of the motor.
  • the leaf spring F When the cylinders are pressurised however, the leaf spring F will yield resiliently to allow the pistons to be moved radially-outwardly by the fluid pressure acting on 'them,'to positions in which their rollers'D engage and drive the cam, as shown at C, D in the case of the cylinder 2in FIG. 2.
  • the spring yields by radial expansion, its overlapped end portions sliding circumferentially relatively to one another.
  • the leaf spring F con-' tracts radially to withdraw all the piston-and-follow'er assemblies once more to their innermost positionsclear of the path of the relatively-rotating cam.
  • the leaf spring co-operates with'the pistons of two adjacent banks of cylinders, opposite edges of the spring acting resiliently on all the cylinders in the respective banks.
  • the spring F'need not act on each piston via a small trapped or journalled roller, but might bear directly against a surface of the body of the piston itself;
  • the leaf spring would be,arranged in aninternal groove in the cylinder block to bear resiliently outwardlyon the piston-and-follower assemblies, so as to retract them radially-outwardly away from the cam when the cylinders were not pressurised.
  • FIGS, 3 to 5 show in greater detail another construction of hydrostaticmotor embodying the presentinvention, the motor being suitable for the direct drive of a vehicle road or land wheel, and comprising a nonrotatable cylinder block 11 bolted to a back plate 12, by means of bolts 13, and a rotatable hub assembly 14 providing a wheel ,flange 15 to which a wheel can be bolted, the hub assembly 14 being rotatably mounted in bearings 16, 17 on the back plate 12 and cylinder.
  • the cylinder block 11 isformed with twelve radial cylinders 20, arranged in two axially-spaced. banks each of six cylinders at 60 spacings, the cylinders 20 being open at their radiallyouter ends and each being provided with an inlet and discharge port 21 at its inner end which co-operates with aring of ports formed in a pintle 25 rotatable with the hub assembly 14in a coaxial central bore 26 in the cylinder block 11, whereby the cyclic admission and discharge of hydraulic fluid to'and from the cylinders is controlled in known 'manner as the hub assembly rotates.
  • the pintle 25 is a close fit in the bore 26 in which it rotates'sthe pintle being keyed at 27 to a central spigot block 28 bolted by bolts 29 to a dished end cover plate 30 of the hub assembly 14.
  • the cover plate 30 is bolted by bolts 31 to the rotary motor housing 18 of the hub assembly, and its spigot block 28 is journalled by means of the bearing 17 in one end of the fixed cylinder block 11.
  • the pintle 25 thus rotates with the hub assembly 14 and in the bore 26 in the cylinder block.
  • the pintle 25 is formed with two axially-spaced rings of ports, 32A, 32B and 33A, 333 which respectively cooperate with the ports 21 of the two banks of cylinders 20.
  • T he ports 32A and 32B alternate in their ring and are respectively connected to an inlet gallery 34 and to associated discharge galleries 35, all formed longitudinally in the pintle 25.
  • the ports 33A and 33B also alternate in their ring and are respectively connected to the galleries 34 and 35, as shown.
  • the central inlet gallery 34 leads into a circumferential groove 36 in the pintle surface, the groove 36 being in communication with a passage 37 formed in the back plate 12 and leading from an inlet port 38 for connection to a hydraulic pressure supply line, as shown in FIG. 5.
  • the four discharge galleries 35 all lead into a common circumferential groove 39 formed in the pintle surface, the groove 39 being in communication with a discharge passage 40 formed in the back plate 12 and leading to a discharge port 41 for connection to a hydraulic fluid return line.
  • the cylinder ports 21 are successively brought into alignment with the ports 32A, 32B, or 33A, 33C in the pintle and are thereby successively connected to the hydrostatic supply pressure and to the return pressure.
  • each cylinder 20 is a cylindrical piston 50 formed in its outer end face with aconcave recess 51 lined by apart-cylindrical bearing shell 52 whose axis extends parallel tothe axisofrotation 53 of the hub.
  • Journalled in the bearing 52 in each piston 50 is a cylindrical roller 55, part of whose cylindrical surface protrude's'outwardly from the piston bearing shell 52 and co-acts with a circumferential cam track 56 formed internally in the motor housing 18 for rotation with the hub assembly 14, and surrounding the cylinder block 1 1.
  • cam tracks 56 spaced apart axially and co-acting with the rollers 55 of the pistons 50 of the respective two banks of cylinders.
  • Each bearing shell 52 has'a small lubrication port in its base which communicates via a passage 58 (FIG. 3) through the recessed piston crown with the interior of the associated cylinder 20, whereby pressure fluid from the cylinder 20 is fed to the bearing 52 to lubricate its bearing surface.
  • the pistons 50 are biassed radially inwardly in the associated cylinders 20 by a circular leaf spring which lies in a circumferential groove 71 formed in the cylinder block 11, and in addition fluid at low hydraulic pressure fills the interior of the housing 18 and acts on the pistons 50 to bias them radially inwardly.
  • the rollers 55 are positively retained in their bearings 52 and prevented from separating radially from the pistons by the shape of the bearings themselves.
  • each bearing shell 52 subtends an angle of about 245 at the axis of the' roller 55, so that the opposite side portions of the bearing shell 52 extend partially around the outer semicylindrical isurface of the roller 55, as shown in the" drawings.
  • the spacing between the longitudinal edges 59 of the bearing is not limited to the bearing.
  • the shell 52 is thus less than the diameter of the roller 55 which is therefore trapped against leaving the shell in the radially-outward direction.
  • the skirts 60 of the piston 50 are similarly formed to extend beyond the level of the axis of the roller, in the outward direction of piston reciprocation, and are inwardlycurved at their outwardly-extending portions to back up-, and'support the bearing shell 52 where this wraps around the roller 55.
  • the followerrollers 55 are positively retained radially in their bearings and are prevented from leaving th'e pistons 50 during free-wheeling of the motor.
  • the follower rollers 55 are also provided with positive end location means to hold them centralised in -their bearings with respect to the axes of their respective cylinder bores and square to the-fcam tracks 56.
  • the outer two guiderings 65 and 67 are axially retained bymeans of spring circlips 68'fitted outside them in shallow circumferential grooves in the cylinder block, to hold the guide rings 65 and 67 in positions slightly overlapping the open ends of thecylinders 20.
  • the guide rings 65 and 67 area free running fit on the cylinder block -11,,so that they'are freely rotatable to reduce rubbing losses between them and the rollers'by reducing the relative speeds of sliding between the rolltwill be seenfrom FIG. 3 that the circuferential I groove 71 formed in the cylinder block 11 intersects the cylinders 20, the walls of the groove 71 being'approximately coplanar with the respectiveinner side faces of the rollers 55 of the two banks'of cylinders.
  • the leaf spring 70 is a'free fit in the groove7l and thus overlaps the margins of the full-diameter cylindrical bodies of the pistons 50.
  • the intersection of the partcylindrical transverse bore 51 in each piston which provides the recess for its follower roller 55 and bearing liner shell 52, with the cylindrical outer surface of the -bo dy of the piston 50 produces a waisted profile of the two skirt portions 60 of the piston, as shown in elevation in FIG. 3, whereby one longitudinal margin of the leaf spring can partially overlie the crown of each piston 50 as shown.
  • each follower roller 55 is less than the full diameter of the piston 50 which carries it, and the leaf spring 70 which as mentioned is a free running fit in the groove 71 lies between the follower rollers 55 of the two banks of cylinders, with the opposite edges of the leaf spring lying in opposed relationship to the adjacent end faces-of the rollers 55 of the respective banks of-cylinders, so that the edges of the leaf spring constitute abutments to provide endwise location of the follower rollers of the respective banks in the axial direction towards one another. Endwise location of the follower rollers in each bank in the direction away from the other bank of cylinders is provided by the respective rotatable guide ring 65 or 67.
  • a peg 72 having a domed upper end is mounted in a small hole 73 formed in the body of each piston 50 at one outer end of the transverse bore 51 and at the radially-lowest part of that bore 51, the peg 72 extending parallel to the axis of the piston 50 in the radially-outward direction with respect to the cylinder block, so that the domed outer end of each peg engages the inner side of the leaf spring 70.
  • the pegs 72 thus take the places of the small rollers E of the preceding embodiment, so that when there is no supply pressure in the inner ends of the cylinders the leaf spring 70 will act resiliently on the pistons'50 via their pegs 72 and will hold the pistons in their fullywithdrawn radially-innermost positions in the cylinders 11, as shown in FIG. 4, in which positions the rollers 55 are just clear of the cam tracks 56, and the motor housing 18 together with thec-am tracks 56 can free-wheel relatiyely to the cylinder block ll without the rollers SS-hitting'thecam tracks.
  • a positive-displacement cam-controlled rotary hy drostatic pressure machine comprising a cylinder block having a bank "of angularly-spaced radial cylinders,
  • each piston comprises a cylindrical roller rotatably mounted in a recess formed in the end of the piston nearest to the cam ring, the roller being prevented from separating radially from the piston, and in which the longitudinal edges of the leaf spring lie in opposed relationship to end faces of the rollers of the respective banks of cylinders, whereby the opposite edges of the leaf spring constitute abutments which provide endwise location for the follower rollers of the respective banks of cylinders.
  • a rotary machine as claimed in claim 1 in which there are two of the said banks of cylinders in the cylinder block, the cylinders in the respective banks being angularly-staggered in relation to one another, and in which the leaf spring is interposed between the two banks of cylinders with the opposite circumferential marginal portions of theleaf spring respectively overlapping the cylinders ofthe two banks and acting on the respective pistonstherein.
  • a rotary machine as claimed in claim 3 in which the cam ring circumferentially surrounds the cylinder block and the leaf spring is located as a free fit in a circumferential groove inthe outer circumference of the cylinder block, the groove intersecting the cylinders of both banks, and in which the follower of each piston comprises a cylindrical roller rotatably mounted in a recess in the end of the piston nearest to the cam ring, the roller being prevented from separating radially from the piston, and in which the longitudinal edges of the leaf lie in opposed relationship to end faces of the rollers ofthe respective banks of cylinders, whereby the opposite'edges of the leaf spring constitute abutments which provide endwise location for the rollers of the respective banks of cylinders.
  • a rotary machine as claimed in claim 4 including spacer rollers freely interposed between the inner face of the leaf spring and each piston, the axes of the spacer rollers being parallel to the axis of the cam ring, and the resilient force of the leaf spring being transmitted radially to each piston through its associated spacer roller. 6.
  • a rotary machine as claimed in claim 4 including 7 a radial peg mounted on each piston to protrude raditrack on the cam ring facing the cylinder block, the pistons carrying followers which co-act with the cam track to convert cyclic radial reciprocating motion of the pistons in the cylinders'into continuous rotary motion of the cam ring relative to the cylinder block, inlet and exhaust ports for high pressure fluid, valve means cyclically controlling the admission of pressurized hydraulic fluid from the inlet port to the cylinders and the discharge of the fluid from the cylinders to the exhaust port in synchronism with the rotary motion of the cam ring relatively to the cylinder block for driving the motor, and a circular leaf spring comprising a flat spring strip curled lengthwise into circular form with its two end portions overlapping one another, the leaf spring being housed in an external circumferential groove in the cylinder block, which groove is positioned between the two banks of cylinders and intersects the cylinders of both banks, and in which the leaf spring overlaps the cylinders of both
  • a motor as claimed in claim 7 including spacer rollers freely interposed between the inner face of theleaf spring and each piston, the axes of the spacer rollers is transmitted to each piston through its associated peg.

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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)
US435955A 1973-04-09 1974-01-23 Radial-piston rotary hydrostatic machines Expired - Lifetime US3913455A (en)

Applications Claiming Priority (1)

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GB1689573A GB1463495A (fr) 1973-04-09 1973-04-09

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US3913455A true US3913455A (en) 1975-10-21

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US (1) US3913455A (fr)
DE (1) DE2417348A1 (fr)
FR (1) FR2224647B3 (fr)
GB (1) GB1463495A (fr)
SE (1) SE395511B (fr)

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3999465A (en) * 1974-11-01 1976-12-28 Clark Equipment Company Magnet piston retention for free wheeling
US4136602A (en) * 1976-05-24 1979-01-30 Lenz Leonard L Hydraulic motor
DE2920588A1 (de) * 1978-05-22 1979-11-29 Poclain Hydraulics Sa Druckmittelmotor
US4522110A (en) * 1982-09-08 1985-06-11 Ab Hagglund & Soner Hydraulic radial piston motor
US4719843A (en) * 1985-05-15 1988-01-19 Societe Anonyme: Poclain Hydraulics Hydraulic mechanism, engine or pump, provided with rollers mounted on the pistons and with members for holding said rollers in position
US5081906A (en) * 1989-09-14 1992-01-21 Poclain Hydraulics Mechanism, motor pump, incorporating pistons supporting, rollers for abutment of said pistons on a cam
US5090295A (en) * 1989-06-14 1992-02-25 Mannesman Rexroth Gmbh Radial piston engine
US5179889A (en) * 1990-02-16 1993-01-19 Mannesmann Rexroth Gmbh Radial piston engine
WO1997032111A1 (fr) * 1996-03-01 1997-09-04 Peter Robert Raffaele Machines fonctionnant a l'aide d'un fluide
US20040194619A1 (en) * 2003-04-01 2004-10-07 Sampo-Hydraulics Oy Radial piston hydraulic motor and method in the control of a radial piston hydraulic motor
CN101858300A (zh) * 2010-06-10 2010-10-13 宁波市恒通液压科技有限公司 内曲线多作用径向柱塞式液压马达
US8256461B1 (en) * 2009-01-30 2012-09-04 Aspen Research, Ltd Distribution valve and cam mechanism
US20130007954A1 (en) * 2009-01-30 2013-01-10 Aspen Research, Ltd. Method and apparatus for cleaning pools with reduced energy consumption
US20150211515A1 (en) * 2011-10-07 2015-07-30 Robert C. Kennedy Micro-Sized Fluid Metering Pump
US20170058879A1 (en) * 2015-09-01 2017-03-02 PSC Engineering, LLC Positive displacement pump
US12085065B2 (en) 2020-10-20 2024-09-10 Golden Bear LLC Pump comprising balls for displacement of fluid

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FR2426801A1 (fr) * 1978-05-22 1979-12-21 Poclain Hydraulics Sa Mecanisme a fluide a glace de distribution axialement mobile
DE3706460A1 (de) * 1986-10-31 1988-09-08 Rexroth Mannesmann Gmbh Kolbenmaschine mit umschaltbarem hubraum
AU3108095A (en) * 1994-09-01 1996-03-22 Soldati Ag Radial piston engine for compressed air operation
FR3128692A1 (fr) * 2021-10-29 2023-05-05 Safran Landing Systems Dispositif d’entraînement en rotation d’une roue comprenant un moteur hydraulique à pistons radiaux et des moyens de verrouillage des pistons en position rentrée.

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US3225701A (en) * 1963-04-04 1965-12-28 Raymond C Griffith Hydraulic pumps
US3270685A (en) * 1962-07-04 1966-09-06 Eickmann Karl Rotary radial piston machine
US3283668A (en) * 1965-03-01 1966-11-08 Suomen Autoteollisuus Ab Oy Hydraulic motor with piston holding means
US3803986A (en) * 1971-11-26 1974-04-16 K Eickmann Rotary radial piston type fluid handling device
US3824899A (en) * 1973-08-22 1974-07-23 Gen Motors Corp Hydraulic motor having a hydraulic lock control drive pin

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3270685A (en) * 1962-07-04 1966-09-06 Eickmann Karl Rotary radial piston machine
US3225701A (en) * 1963-04-04 1965-12-28 Raymond C Griffith Hydraulic pumps
US3283668A (en) * 1965-03-01 1966-11-08 Suomen Autoteollisuus Ab Oy Hydraulic motor with piston holding means
US3803986A (en) * 1971-11-26 1974-04-16 K Eickmann Rotary radial piston type fluid handling device
US3824899A (en) * 1973-08-22 1974-07-23 Gen Motors Corp Hydraulic motor having a hydraulic lock control drive pin

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3999465A (en) * 1974-11-01 1976-12-28 Clark Equipment Company Magnet piston retention for free wheeling
US4136602A (en) * 1976-05-24 1979-01-30 Lenz Leonard L Hydraulic motor
DE2920588A1 (de) * 1978-05-22 1979-11-29 Poclain Hydraulics Sa Druckmittelmotor
US4522110A (en) * 1982-09-08 1985-06-11 Ab Hagglund & Soner Hydraulic radial piston motor
US4719843A (en) * 1985-05-15 1988-01-19 Societe Anonyme: Poclain Hydraulics Hydraulic mechanism, engine or pump, provided with rollers mounted on the pistons and with members for holding said rollers in position
US5090295A (en) * 1989-06-14 1992-02-25 Mannesman Rexroth Gmbh Radial piston engine
US5081906A (en) * 1989-09-14 1992-01-21 Poclain Hydraulics Mechanism, motor pump, incorporating pistons supporting, rollers for abutment of said pistons on a cam
US5179889A (en) * 1990-02-16 1993-01-19 Mannesmann Rexroth Gmbh Radial piston engine
WO1997032111A1 (fr) * 1996-03-01 1997-09-04 Peter Robert Raffaele Machines fonctionnant a l'aide d'un fluide
FR2853364A1 (fr) * 2003-04-01 2004-10-08 Sampo Hydraulics Oy Moteur hydraulique a pistons radiaux, et procede pour sa commande
US20040194619A1 (en) * 2003-04-01 2004-10-07 Sampo-Hydraulics Oy Radial piston hydraulic motor and method in the control of a radial piston hydraulic motor
GB2400417A (en) * 2003-04-01 2004-10-13 Sampo Hydraulics Oy A radial piston motor having a free rotation valve
GB2400417B (en) * 2003-04-01 2006-07-12 Sampo Hydraulics Oy Radial piston hydraulic motor and method in the control of a radial piston hydraulic motor
US7225720B2 (en) 2003-04-01 2007-06-05 Sampo-Hydraulics Oy Radial piston hydraulic motor and method in the control of a radial piston hydraulic motor
US8256461B1 (en) * 2009-01-30 2012-09-04 Aspen Research, Ltd Distribution valve and cam mechanism
US20130007954A1 (en) * 2009-01-30 2013-01-10 Aspen Research, Ltd. Method and apparatus for cleaning pools with reduced energy consumption
US8820355B2 (en) * 2009-01-30 2014-09-02 Aspen Research, Ltd Method and apparatus for cleaning pools with reduced energy consumption
CN101858300A (zh) * 2010-06-10 2010-10-13 宁波市恒通液压科技有限公司 内曲线多作用径向柱塞式液压马达
US20150211515A1 (en) * 2011-10-07 2015-07-30 Robert C. Kennedy Micro-Sized Fluid Metering Pump
US20170058879A1 (en) * 2015-09-01 2017-03-02 PSC Engineering, LLC Positive displacement pump
US10408201B2 (en) * 2015-09-01 2019-09-10 PSC Engineering, LLC Positive displacement pump
US12085065B2 (en) 2020-10-20 2024-09-10 Golden Bear LLC Pump comprising balls for displacement of fluid

Also Published As

Publication number Publication date
SE395511B (sv) 1977-08-15
FR2224647B3 (fr) 1978-02-17
FR2224647A1 (fr) 1974-10-31
GB1463495A (fr) 1977-02-02
DE2417348A1 (de) 1974-10-24

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