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WO2011070019A1 - Machine hydrostatique à pistons radiaux - Google Patents

Machine hydrostatique à pistons radiaux Download PDF

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Publication number
WO2011070019A1
WO2011070019A1 PCT/EP2010/069078 EP2010069078W WO2011070019A1 WO 2011070019 A1 WO2011070019 A1 WO 2011070019A1 EP 2010069078 W EP2010069078 W EP 2010069078W WO 2011070019 A1 WO2011070019 A1 WO 2011070019A1
Authority
WO
WIPO (PCT)
Prior art keywords
radial
cylinder star
control
mirror body
control mirror
Prior art date
Application number
PCT/EP2010/069078
Other languages
German (de)
English (en)
Inventor
Jürgen Berbuer
Original Assignee
Berbuer Juergen
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Berbuer Juergen filed Critical Berbuer Juergen
Priority to EP10790918.6A priority Critical patent/EP2510192B1/fr
Priority to CN201080056016.4A priority patent/CN102652206B/zh
Publication of WO2011070019A1 publication Critical patent/WO2011070019A1/fr
Priority to US13/493,188 priority patent/US9784252B2/en

Links

Classifications

    • 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
    • F04B1/063—Control by using a valve in a system with several pumping chambers wherein the flow-path through the chambers can be changed, e.g. between series and parallel flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0403—Details, component parts specially adapted of such engines
    • F03C1/0435—Particularities relating to the distribution members
    • F03C1/0444—Particularities relating to the distribution members to plate-like distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B13/00—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion
    • F01B13/04—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder
    • F01B13/06—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement
    • F01B13/061—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement the connection of the pistons with the actuated or actuating element being at the outer ends of the cylinders
    • F01B13/062—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement the connection of the pistons with the actuated or actuating element being at the outer ends of the cylinders cylinder block and actuating or actuated cam both rotating
    • 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
    • F04B1/0404—Details or component parts
    • F04B1/0452—Distribution members, e.g. valves
    • F04B1/0465—Distribution members, e.g. valves plate-like
    • 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
    • F04B1/10—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary
    • F04B1/107—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders
    • F04B1/1071—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders with rotary cylinder blocks
    • 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
    • F04B1/10—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary
    • F04B1/107—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders
    • F04B1/1071—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders with rotary cylinder blocks
    • F04B1/1072—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders with rotary cylinder blocks with cylinder blocks and actuating cams rotating together

Definitions

  • the invention relates to a hydrostatic radial piston machine comprising a housing, a cylinder star rotatably mounted in the housing about an axis of rotation and having a number of bores which extend from an outer surface of the cylinder star into its interior and are distributed over its circumference, one of the number of holes corresponding number of pistons which are slidably disposed in the bores and each define a working space for a hydraulic fluid together with the associated bore, an eccentrically arranged to the cylinder star cam ring which surrounds the cylinder star circumferentially and on the inner circumferential surface itself the cylinder star facing away from the piston during the rotational movement of the cylinder star movably support, two control mirror bodies having a total of at least two control cross sections, at least one of which with the inlet channel and at least one other with the off Lasskanal communicates, wherein both control mirror bodies each extend with a cylindrical face facing the end face on a plane perpendicular to the axis of rotation of the cylinder star to a plane beyond, from
  • Radial piston machines i. Radial piston pumps and radial piston motors can be subdivided, inter alia, according to how soft the hydraulic fluid is supplied to the work spaces in the cylinder star.
  • From EP-A-0 401 408 it is known that the supply and discharge of the hydraulic fluid over a stationary, i. connected to the housing so-called control pin is done. Disadvantages of this very widespread design are that only relatively narrow flow channels (inlet and outlet channel) can be realized within the control pin and that due to the axially out of the control pin flow channels, the mechanical bending load of the control pin is quite high.
  • the bearing of a drive or output shaft is hardly loaded.
  • a radial piston machine of the type described above is known for example from US-A-3,951,044.
  • the machine disclosed therein has two control mirror bodies which are arranged on opposite sides of the cylinder star and which have a spherical shape on the side facing the cylinder star which interacts with an analogous calotte-shaped shape of the opposite side surfaces of the cylinder star (see FIG. in particular the local figure 4).
  • at least one control mirror body is limited in all directions, ie both in the axial and in the radial direction, movable.
  • the rotating shaft connected to the cylinder star has to absorb the radial forces arising during operation due to the hydraulic pressures. This in turn leads to increased construction costs for the shaft and its storage and to potential wear.
  • the object of the invention is to propose a radial piston machine in which the hydraulic forces can be fully hydrostatically relieved and stably supported.
  • each control plate body has a bearing area in which radially acting forces can be transmitted to a respective mating surface in the housing or a housing cover mounted therein.
  • a control-plate body can be understood as meaning either a separate component in comparison with the housing, or a design integrally connected to the housing or a housing cover.
  • a control mirror body must not be traversed by the hydraulic fluid, which may be the case when in a single control mirror body both control cross sections, ie both for the supply and the discharge of the hydraulic fluid from the cylinder chambers, whereas the other control mirror body no function in relation to fulfills the fluid supply of the cylinder star.
  • the term control mirror body is therefore geometrically and mechanically understood in the present sense and not necessarily in relation to a flow of hydraulic fluid. Decisive is an abutment against the cylinder star in the axial direction.
  • the invention is - viewed in the axial direction - not only an intervention of the two control mirror body in the cylinder star before, but also a derivative of the radial forces on the control mirror body.
  • these thus overlap, with the control plate bodies projecting in a region lying radially further in the direction of the axial center of the cylinder star, so that a region of the cylinder stem located radially further outwardly virtually covers the two control plate bodies.
  • Due to the inventive storage of the control mirror body is a complete hydrostatic discharge of the hydraulic forces occurring during operation and a stable support thereof via the housing or the housing cover, possible.
  • each control disk body extending into the cylinder star thus fulfills the function of a "collar" known from architecture, figuratively speaking and in an axial section view, whereas in each case the area of the cylinder star, in which the width is radially outward - increases as a species
  • Capstone acts, which converts radial compressive forces in a pair of oppositely biased forces, the radial component in turn are each derived from the opposite control mirror bodies in this superimposed housing or housing cover.
  • control mirror body at radially extending separation level in the control cross sections ie in the interface between the control mirror body and cylinder star, disc-shaped and have only perpendicular to the axis of rotation extending end surfaces. Due to this design, a support during operation occurring radial forces on the control mirror body is impossible. The same applies to spherical see or conical / conical control mirror body, but can not transmit any radial forces on the housing or its cover for lack of appropriate storage.
  • the invention provides a remedy by the intermeshing of the cylinder star and the control disk body and their mounting in the housing or housing cover, which leads to a particularly high compressive strength of the radial piston engine according to the invention.
  • a further advantage of the invention is the great robustness of the machine in the case of pressure surges and vibrations, since a closed power flow takes place involving the typically very rigid machine housing, which in turn results in a low noise emission. Due to the complete hydrostatic discharge of the hydraulic forces, the machine according to the invention is also suitable for poorly lubricating media, ie in particular for use in the so-called "water hydraulics".
  • the cylinder star has at least one support region in which the axial width is smaller than in a free-wheeling region which adjoins the support region in the radial direction, wherein at least one control cross-section of the control-plate body is preferably located in the support region.
  • at least one control plate body has a support region corresponding to the support region of the cylinder star and a storage region facing away from the support region in the radial direction outwardly adjoining the support region and / or in the axial direction.
  • the respective control plate body is accommodated in a housing or housing cover, so that the forces introduced by the cylinder star into the control plate body can be dissipated further into the housing or the housing cover.
  • the support region preferably extends from a central torque coupling region (eg in the form of a multi-tooth bore or a journal) in the radial direction up to a diameter which is approximately 60% to 90%, preferably 70% to 80%, of the maximum diameter of the cylinder star.
  • a central torque coupling region eg in the form of a multi-tooth bore or a journal
  • a particularly favorable geometry of the control plate body is present if this has a conical, conical-ring-shaped or convex, in particular spherical, curved shape, wherein preferably the support region is designed conical, conical-shaped or convex, in particular spherical, arched.
  • the adjoining in the axial direction storage area which may have a larger diameter than the support area, then preferably a cylindrical shape, resulting in a particularly simple storage in the housing or the housing cover.
  • the cone angle should be between 90 ° and 150 °, preferably between 1 10 ° and 130 ° and more preferably 120 °, since this is an equiangular triangle of forces with an angle between the radially acting pressure force and the oblique supporting forces of each gives 120 °.
  • the optimum cone angle in each case results from the respective diameters at the beginning and at the end of the conical section and the number of working spaces distributed over the circumference of the cylinder star and can be computationally exact according to the known rules of hydraulics under the premise of a complete hydraulic balance of forces determine.
  • the invention further ausgestaltend it is proposed that the cylinder star and at least one control mirror body in the axial direction patrizen-matrizen-shaped mesh.
  • a respective control mirror body is arranged on both sides of the cylinder star, one of them should be biased in the direction of the opposite control mirror body by means of a spring element supported on a housing or a housing cover, preferably a corrugated spring.
  • This provides axial gap compensation, i. Tightness, in the region of the separation plane between the control mirror body and the cylinder star, in particular in the area of the control cross sections achieved.
  • control channels of two opposing control mirror body and an interposed passageway of the cylinder star are aligned, preferably form a continuous cylindrical bore with a constant cross section.
  • the control channels are unused in a control disk body which is not used for hydraulic fluid supply or exhaust, but this is in no way disadvantageous.
  • each piston head of the piston is designed cup-shaped in longitudinal section and with no interposition of a separate sealing element a cup rim sealed to an internal ren shell surface of the respective bore of the cylinder star rests, wherein the pistons are preferably made of plastic and more preferably are plastic injection molded parts.
  • the cup rim has a depth seen in the axial direction of the piston and a thickness seen in the radial direction, which ensures that the fluid pressure in the working space, taking advantage of the component elasticity, ensures sufficient surface pressure between the cup rim outer casing and the bore casing surface.
  • FIG. 2a is an enlarged view of the cylinder star and the control disk body according to FIG. 2, FIG.
  • FIG. 3 shows a cross section through a second embodiment of a radial piston machine with a piston in the shape of a cup, as in FIG. 3, but in longitudinal section and
  • Fig. 5 as Figure 1, but with illustrated by arrows force vectors
  • a radial piston machine 1 shown in FIGS. 1, 2 and 2a comprises a housing 2, which-viewed in the axial direction-is closed in a fluid-tight manner on one side with a housing cover 3.
  • a cam ring 4 is slidably mounted and along each two planar surfaces 5 and 6, which are formed on the one hand on an inner circumferential surface 7 of the housing 2 and on the other hand on an outer circumferential surface 8 of the cam ring.
  • the radial piston machine 1 has a rotor in the form of a so-called cylinder star 9, which is rotatable about a rotation axis 10.
  • the cylinder star 9 has nine bores 11 arranged equidistantly around its circumference, which, starting from an outer circumferential surface 12 of the cylinder star 9, penetrate radially into its interior, i. on the axis of rotation 10 to extend.
  • each piston 13 is slidably disposed, each piston 13 has a piston head 14, with which it is sealed in the bore 1 1 mounted, and a plate-shaped piston 15, with the lower end face 16 of the respective piston thirteenth is supported on a spherically curved inner lateral surface 17 of the cam ring 4.
  • Each piston 13 has a from the piston head 14 to the piston 15 extending through bore 18 which opens at the end face 16 of the piston 15 in a pressure chamber 19, which in turn leads to a hydrostatic relief of the bearing of the piston 15 on the lifting ring 4.
  • each piston 13 has in the region of its piston head 14 a circumferential groove into which a piston ring 20 is inserted for sealing purposes.
  • the axis of rotation 10 of the cylinder star 9 and the center axis of the cam ring 4 are arranged eccentrically to each other, wherein the (variable) amount of eccentricity the stroke of Piston 13 defined.
  • the pistons 13 therefore move from a top dead center, where they are immersed in the deepest hole 1 1, to a bottom dead center, where they together with the walls of the Bore 1 1 limit a maximum work space 22 then.
  • the extent of eccentricity between cylinder star 9 and cam 4 can be varied in the present case with the aid of two hydraulic actuating cylinder, the cylinder bores 23 and 24 are located on opposite sides of the housing 2 and each with an axially displaceable in the cylinder bore 23, 24 mounted cup-shaped piston 25, 26 are provided. Starting from the position shown in Figure 1, in which the eccentricity is maximum leaves the cam 4 (parallel to the flat surfaces 5 and 6) to move the way to the right 27, whereby the eccentricity and thus the delivery rate of the radial piston machine is reduced to zero.
  • control mirror body 30 is located between a housing wall 31 and the cylinder star 9.
  • Another, substantially identical shaped control mirror body 32 is located on the opposite side of the cylinder star 9 and is bounded on its side facing away from the cylinder star 9 by a housing wall 33.
  • control channel 29, 34 in a cylinder star 9 facing end face of the control mirror body 30, 32 extends in a circular segment.
  • This known design makes it possible for the hydraulic fluid to flow into the respective working chamber 22 from the control channel 29 via a respective passageway 35 assigned to each cylinder bore 9 in the suction chamber during an intake phase extending over an angular range of approximately 150 °.
  • the flow connection between the control channel 29 assigned to the inlet channel 28 and the associated passage channel 35 ends, whereas at the next moment a connection exists between the further control channel 37 constructed like the control channel 29 and an outlet channel 36 the "pressure side" of the control mirror body 30 and the radial piston machine 1 is produced.
  • the cross sections of the control channels 29, 37, which are arranged in the respective separation planes between the control mirror body 30 and the cylinder star 9 are referred to as control cross sections 29 ', 37'.
  • Control plate body 32 shown on the right also has a second, ie lower, control channel 38, which in the present case - as well as the upper control channel 34 of this control mirror body 32 - is inoperative.
  • the suction-side control channel 34 of the control plate body 32 can likewise be connected to the inlet channel 28.
  • the connection of the control channel 38 with the outlet channel 36 is hardly required;
  • both control mirror body 30, 32 are each provided with two control channels 29, 37 and 34, 38.
  • spring element 39 in the form of a rotating wave spring.
  • a pressure-compensated compensation surface K is additively provided on the end face of the cover 3 facing the control mirror body 32.
  • This compensation surface K is twice kidney-shaped and corresponds on the one hand with the suction-side control channel 29 and the other with the pressure-side control channel 37.
  • a kidney-shaped sealing element D is a corresponding with the compensation surface K volume between the housing cover 3 and this facing the back End face of the control mirror body 32 sealed.
  • Both Steueraptköper 30, 32 each have a conical-ring-shaped support portion 40, 41 which cooperates with a complementarily shaped, also cone-shaped support portion 42, 43 on the opposite end faces of the cylinder star 9. While the control channels 29, 37 and 34, 38, ie, in particular also the control cross sections 29 ', 37', are located in the support regions 40, 41 of the control plate bodies 30, 32, the control elements extend as through-holes. Passage holes executed passageways 35 in the mutual support areas 42 and 43 of the cylinder star. 9
  • Both control mirror bodies 30, 32 each have a central through-bore 44, 45 through which runs a drive shaft 46 of the radial piston machine 1.
  • a torque coupling region 47 of the cylinder star 9 is designed as a hexagon socket, in which a correspondingly adapted external hexagon of the drive shaft 46 is inserted in a rotationally fixed manner.
  • Both control plate bodies 30, 32 have a cylindrical-ring-shaped bearing region 48, 49 adjoining the respective support region 40, 41 in the radial direction, the outer lateral surface 50, 51 of which is respectively mounted in a matched recess in the housing 2 or the housing cover 3 is.
  • the cylinder star 9 has a - viewed in the radial direction - at the support areas 42 and 43 subsequent freewheeling 52, 53, in which between the respective end face 54, 55 of the cylinder star 9 and the opposite end face 56, 57 of the control mirror body 30, 32nd in each case a gap 58, 59 is located.
  • the width of the cylinder star 9 measured in the axial direction decreases in the support areas 42, 43 towards the axis of rotation 10.
  • the largest axial width 60 is in the freewheeling region 52, 53, whereas the smallest axial width 61 is in the torque coupling region 47.
  • the cone angle of the control plate body 30, 32 is 120 °, so that the track straight of the drawing section plane with the control mirror bodies 30, 32 with the axis of rotation 10 each enclose an angle of 60 °.
  • control mirror bodies 30, 32 with their conical-ring-shaped end faces forming the support regions 42, 43 extend beyond the planes formed by the end faces 54, 55 of the cylinder star 9 in the direction of a center plane 62 of the cylinder star perpendicular to the rotation axis 10 9 extend.
  • the difference between the radial piston machine 1 shown in FIGS. 3 and 4 is that the pistons 13 'have a cup-shaped configuration there in longitudinal section.
  • a in the respective piston head 14 'arranged cup edge 63 has a small, towards the free end of the cup rim 63 toward decreasing wall thickness, so that as a result of a pressure build-up in the working space 22 of the respective bore 1 1 in the cylinder star 9 a self-reinforce- the sealing effect occurs.
  • the pistons 13 ' are made as plastic injection molded parts and consist for example of PEEK (poly ether ether ketone) or PAI (poly amide imide).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)

Abstract

L'invention concerne une machine hydrostatique à pistons radiaux présentant une étoile de cylindres (9) avec des alésages de cylindres (11) qui partent d'une surface d'enveloppe extérieure de l'étoile de cylindres, s'étendent à l'intérieur de celle-ci et sont disposés de façon répartie sur son pourtour ; un nombre de pistons (13) correspondant au nombre des alésages de cylindres ; une bague de levage (4) disposée de façon excentrée par rapport à l'étoile de cylindres, qui entoure de façon périphérique l'étoile de cylindres et sur la surface d'enveloppe intérieure (17) de laquelle s'appuient de façon mobile des extrémités, opposées à l'étoile de cylindres, des pistons pendant le mouvement de rotation de l'étoile de cylindres ; et deux corps de miroir de commande (30, 32), qui s'étendent respectivement avec une surface frontale tournée vers l'étoile de cylindres sur un plan médian, perpendiculaire à l'axe de rotation, de l'étoile de cylindres au-delà d'un plan qui est défini par une surface frontale, tournée vers le corps de miroir de commande respectif, de l'étoile de cylindres à son emplacement présentant la plus grande largeur axiale. Chaque corps de miroir de commande présente une zone de palier, dans laquelle des forces agissant radialement peuvent être transmises à une contre-surface respective dans le boîtier (2) ou un couvercle de boîtier (3) montés dans celui-ci.
PCT/EP2010/069078 2009-12-11 2010-12-07 Machine hydrostatique à pistons radiaux WO2011070019A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP10790918.6A EP2510192B1 (fr) 2009-12-11 2010-12-07 Machine hydrostatique à pistons radiaux
CN201080056016.4A CN102652206B (zh) 2009-12-11 2010-12-07 静液压径向活塞机
US13/493,188 US9784252B2 (en) 2009-12-11 2012-06-11 Hydrostatic radial piston machine

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009054548.4 2009-12-11
DE102009054548A DE102009054548A1 (de) 2009-12-11 2009-12-11 Hydrostatische Radialkolbenmaschine

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US13/493,188 Continuation US9784252B2 (en) 2009-12-11 2012-06-11 Hydrostatic radial piston machine

Publications (1)

Publication Number Publication Date
WO2011070019A1 true WO2011070019A1 (fr) 2011-06-16

Family

ID=43662907

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2010/069078 WO2011070019A1 (fr) 2009-12-11 2010-12-07 Machine hydrostatique à pistons radiaux

Country Status (5)

Country Link
US (1) US9784252B2 (fr)
EP (1) EP2510192B1 (fr)
CN (1) CN102652206B (fr)
DE (2) DE102009054548A1 (fr)
WO (1) WO2011070019A1 (fr)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
DE102014215255A1 (de) 2013-08-07 2015-02-12 Schaeffler Technologies Gmbh & Co. Kg Radialkolbenmaschine

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Publication number Priority date Publication date Assignee Title
DE102009054548A1 (de) 2009-12-11 2011-06-16 Berbuer, Jürgen, Dr.-Ing. Hydrostatische Radialkolbenmaschine
DE102011115272A1 (de) 2011-09-29 2013-04-04 Robert Bosch Gmbh Hydrostatische Radialkolbenmaschine
DE102012008623A1 (de) * 2012-04-28 2013-10-31 Robert Bosch Gmbh Radialkolbenmaschine
WO2018205015A1 (fr) * 2017-05-06 2018-11-15 Kinetics Drive Solutions Inc. Variateur hydrostatique basé sur des machines à pistons radiaux
US10982670B2 (en) * 2019-01-22 2021-04-20 GM Global Technology Operations LLC Gear pump and gear assembly

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DE1653371A1 (de) * 1966-12-08 1971-01-28 Breinlich Dr Richard Maschinen mit fluiddurchstroemten Arbeitskammern axialwaertiger Fluidbeaufschlagung
US4624174A (en) * 1982-01-29 1986-11-25 Karl Eickmann Multiple stroke radial piston machine having plural banks of cylinders and fluid pressure pockets on the pistons
US5152579A (en) 1989-04-17 1992-10-06 Mccord Winn Textron Inc. Pumping system for the back support of a seat
CN2103025U (zh) * 1991-09-29 1992-04-29 周其宁 双斜盘大流量柱塞油泵
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EP2510192A1 (fr) 2012-10-17
US20130145929A1 (en) 2013-06-13
CN102652206A (zh) 2012-08-29
CN102652206B (zh) 2014-12-24
DE202010013078U1 (de) 2011-02-24
DE102009054548A1 (de) 2011-06-16
US9784252B2 (en) 2017-10-10
EP2510192B1 (fr) 2013-06-26

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