EP2510192B1 - Machine hydrostatique à pistons radiaux - Google Patents

Machine hydrostatique à pistons radiaux Download PDF

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Publication number
EP2510192B1
EP2510192B1 EP10790918.6A EP10790918A EP2510192B1 EP 2510192 B1 EP2510192 B1 EP 2510192B1 EP 10790918 A EP10790918 A EP 10790918A EP 2510192 B1 EP2510192 B1 EP 2510192B1
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EP
European Patent Office
Prior art keywords
cylinder star
control mirror
control
mirror body
star
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EP10790918.6A
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German (de)
English (en)
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EP2510192A1 (fr
Inventor
Jürgen Berbuer
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Individual
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Individual
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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

  • Radial piston machines ie radial piston pumps and radial piston motors, can be subdivided among other things according to how the hydraulic fluid is supplied to the work spaces in the cylinder star.
  • control pin a stationary, ie connected to the housing so-called control pin.
  • 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 engine of the type described above and with the features of the preamble of claim 1 is for example from the US-A-3,951,044 known.
  • the disclosed therein machine has two arranged on opposite sides of the cylinder star control mirror body, which have on the side facing the cylinder star a spherical shape, which cooperates with an analogous dome-shaped shape of the opposite side surfaces of the cylinder star (s. especially the local ones FIG. 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 spider must 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 invention has for its object to propose a radial piston engine, in which the hydraulic forces can be fully hydrostatically relieved and stably supported.
  • each control mirror body has a bearing region in which radially acting forces on a respective mating surface in the housing or a housing cover mounted therein are transferable.
  • 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 the fluid supply of the cylinder star is met.
  • 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 with 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, wherein the control mirror body protrude in a radially further inner region in the direction of the axial center of the cylinder star, whereby a radially further outward region of the cylinder star covers the two control mirror body quasi.
  • 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 - figuratively speaking and in an axial section view - the function of a "collar” known from architecture, whereas in each case the area of the cylinder star in which the width increases - when viewed radially outwards acts as a kind of "capstone” that converts radial compressive forces into a pair of oppositely biased forces, the radial components of which are in turn derived respectively from the opposed control disc bodies into the housing or housing cover which supports them.
  • control mirror body at radially extending separation level in the control cross sections ie in the region of the interface between the control mirror body and cylinder star, disc-shaped and have only perpendicular to the axis of rotation extending end faces. Due to this design, a support during operation occurring radial forces on the control mirror body is impossible. The same applies to spherical ones 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 by the interengagement of cylinder star and control plate body and their storage in the housing or housing cover, remedy, resulting in a particularly high compressive strength of the radial piston engine according to the invention.
  • the great robustness of the machine is to look at pressure surges and vibrations, as a closed power flow 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 110 ° 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 obliquely directed supporting forces of each 120 ° results.
  • 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 sealing at an inner Mantle 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.
  • FIGS. 1 . 2 and 2a illustrated radial piston machine 1 comprises a housing 2, which - viewed in the axial direction - is closed fluid-tight 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 in this case nine equidistantly distributed over its circumference arranged holes 11, which, starting from an outer circumferential surface 12 of the cylinder star 9 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 11 is mounted, and a plate-shaped piston foot 15, with the lower end face 16 of the respective piston 13 at a spherical curved inner lateral surface 17 of the cam ring 4 is supported.
  • 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. Between the piston head 14 and the piston 15 there is a reduced diameter piston neck, which - depending on the position of the piston 13 in the bore 11 - allows tilting of the piston longitudinal axis to the bore longitudinal axis.
  • 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 11, to a bottom dead center, where they together with the walls of the bore 11 a then limit maximum working space 22.
  • the extent of eccentricity between the cylinder star 9 and cam 4 can be varied in the present case with the aid of two hydraulic adjusting cylinders, the cylinder bores 23 and 24 are located on opposite sides of the housing 2 and each with an axially in the cylinder bore 23, 24 slidably mounted cup-shaped Pistons 25, 26 are provided. Starting from the in FIG. 1 shown position 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 cross sections 29 ', 37' are referred to as control cross sections 29 ', 37'.
  • each piston 13 pushes the hydraulic fluid in the associated working space 22 through the passage channel 35 associated with each bore 11 and the control channel 37 extending over a circular segment of approximately 150 ° into the outlet channel 36.
  • the passageways 35 each in two intermediate areas between the control cross sections 29 'and 37' close to a short circuit between To prevent suction and pressure side.
  • 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.
  • 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.
  • kidney-shaped sealing member D is a corresponding with the compensation surface K volume between the housing cover 3 and the rear side facing this End face of the control mirror body 32 sealed.
  • a pressure-proportional axial contact force is generated, which is always only a few percent above the axial component of the hydraulic splitting force on the respective control mirror body 30, 32.
  • the gap compensation is ensured without generating large "excess forces", which would only lead to increased friction.
  • 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 in the support areas 40, 41 of the control mirror body 30, 32, the control channels 29, 37 and 34, 38, ie in particular also the control cross sections 29 ', 37', which are as through 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 I ⁇ oppel Scheme 47 of the cylinder star 9 is designed as a hexagon socket, in which a suitably 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.
  • FIG. 2a It can be seen that the measured in the axial direction width of the cylinder star 9 in the support areas 42, 43 to the rotation axis 10 decreases.
  • 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 in the FIGS. 3 and 4 shown radial piston machine 1 is that the piston 13 'there have a cup-shaped shape 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 towards decreasing wall thickness, so that as a result of a pressure build-up in the working chamber 22 of the respective bore 11 in the cylinder star 9 a self-reinforcing 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).
  • the piston 13 ' are rotationally symmetrical components, wherein the plastic material used elastically in its contact area with the inner circumferential surface of the bore 11 allows a change in shape, as a result of the inclination of the piston 13' during rotation of the cylinder star 9, the contact line in the area the piston head 14 'describes an ellipse.

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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)

Claims (11)

  1. Moteur à pistons radiaux hydrostatique (1) comportant :
    - un logement,
    - un barillet à pistons radiaux (9) positionné rotativement autour d'un axe de rotation (10) dans le logement (2), qui possède une pluralité d'alésages (11), qui s'étendent à partir d'une surface de gaine extérieure (12) du barillet à pistons radiaux (9) à l'intérieur de celui-ci et sont répartis sur la circonférence de celui-ci,
    - une pluralité de pistons (13, 13') correspondant à la pluralité d'alésages (11), qui sont disposés de manière déplaçable dans les alésages (11) et délimitent respectivement conjointement à l'alésage coordonné (11) un espace de travail (22) pour un fluide hydraulique,
    - une couronne de levage (4) disposée excentriquement au barillet à pistons radiaux (9), qui entoure la circonférence du barillet à pistons radiaux (9) et, sur la surface de gaine intérieure (17) de celui-ci, s'appuient de manière mobile les extrémités du piston (13, 13') qui se détournent du barillet à pistons radiaux (9) pendant le mouvement de rotation du barillet à pistons radiaux (9),
    - deux corps de plaque de commande (30, 32), qui présentent au total au moins deux sections transversales de commande, desquels au moins un est relié au canal d'admission (28) et au moins un autre est relié au canal d'échappement (36), dans lequel les deux corps de plaque de commande (30, 32) s'étendent respectivement par une surface frontale tournée vers le barillet à pistons radiaux (9) sur un plan central (62) du barillet à pistons radiaux (9) perpendiculaire à l'axe de rotation (10) jusqu'à un plan, qui est défini par une surface frontale (54, 55) du barillet à pistons radiaux (9) tournée vers le corps de plaque de commande respective (30, 32)à l'emplacement de celui-ci avec la plus grande largeur axiale (60),
    - une pluralité de canaux de passage (35) disposés dans le barillet à pistons radiaux correspondant à la pluralité d'alésages (11) du barillet à pistons radiaux (9), qui - en fonction de la position de rotation du barillet à pistons radiaux (9) dans la couronne de levage (4) - relient respectivement un espace de travail (22) avec une section transversale de commande correspondant au canal d'admission (28) ou avec une section transversale de commande correspondant au canal d'échappement (36) ou peuvent être obturés par une surface d'obturation se trouvant sur le corps de plaque de commande (30, 32),
    caractérisé en ce que chaque corps de plaque de commande (30, 32) présente une surface de palier (48, 49), dans laquelle des forces agissant radialement peuvent être transmises sur une surface opposée respective dans le logement (2) ou un couvercle de logement (3) positionné dans celui-ci.
  2. Moteur à pistons radiaux selon la revendication 1, caractérisé en ce que le barillet à pistons radiaux (9) présente au moins une zone d'appui (42, 43), dans laquelle la largeur axiale est plus petite que dans une zone de mise en roue libre (52) se rattache dans la direction radiale à la zone d'appui (42, 43) en allant vers l'extérieur, dans lequel de préférence dans la zone d'appui (42, 43) se trouve au moins une section transversale de commande du corps de plaque de commande (30, 32), dans lequel de préférence au moins un corps de plaque de commande (30, 32) présente une zone d'appui (40, 41) correspondant à la zone d'appui (42, 43) du barillet à pistons radiaux (9), dans lequel de préférence se rattache la zone de palier respective (48, 49) soit à la zone d'appui (40, 41) dans la direction radiale en allant vers l'extérieur et/ou soit dans la direction axiale qui se détourne de la zone d'appui (40, 41).
  3. Moteur à pistons radiaux selon la revendication 2, caractérisé en ce que la zone d'appui (42, 43) du barillet à pistons radiaux (9) s'étend de préférence à partir d'une zone d'accouplement à couple de rotation (47) centrale dans la direction radiale jusqu'à un diamètre, qui correspond environ à 60% à 90%, de préférence à 70% à 80% du diamètre maximal du barillet à pistons radiaux (9).
  4. Moteur à pistons radiaux selon une des revendications 1 à 3, caractérisé en ce que le corps de plaque de commande (30, 32) possède une forme bombée conique, de bague conique ou convexe, notamment sphérique, dans lequel de préférence la surface d'appui (40, 41) a une forme bombée conique, de bague conique ou convexe, notamment sphérique.
  5. Moteur à pistons radiaux selon la revendication 4, caractérisé en ce que l'angle de conicité est compris entre 90° et 150°, de préférence entre 110° et 130°.
  6. Moteur à pistons radiaux selon une des revendications 1 à 5, caractérisé en ce que le barillet à pistons radiaux (9) et au moins un corps de plaque de commande (30, 32) viennent en prise l'un dans l'autre dans la direction radiale en forme de poinçon/matrice.
  7. Moteur à pistons radiaux selon une des revendications 1 à 6, caractérisé en ce que les deux corps de plaque de commande (30, 32) sont déplaçables l'un par rapport à l'autre dans la direction axiale, de préférence en ce que un des corps de plaque de commande (32) est déplaçable dans la direction axiale par rapport au logement (3) ou au couvercle de logement (3), tandis que l'autre corps de plaque de commande (30) est immobilisé dans la direction axiale dans le logement (2) ou le couvercle de logement (3).
  8. Moteur à pistons radiaux selon une des revendications 1 à 7, caractérisé en ce que un corps de plaque de commande (30, 32) est respectivement disposé des deux côtés du barillet à pistons radiaux (9), dans lequel un corps de plaque de commande (32) est précontraint au moyen d'un élément de ressort (39) s'appuyant sur le logement (2) ou sur le couvercle de logement (3), de préférence un ressort ondulé, dans la direction du corps de plaque de commande (30) opposé.
  9. Moteur à pistons radiaux selon une des revendications 1 à 8, caractérisé en ce que des canaux de passage (35) du barillet à pistons radiaux (9) correspondant respectivement à un espace de travail (22) s'étendent respectivement depuis une zone d'appui jusqu'à la zone d'appui opposée (42, 43).
  10. Moteur à pistons radiaux selon une des revendications 1 à 9, caractérisé en ce que des canaux de commande (29, 34, 37, 38) de deux corps de plaque de commande (30, 32) opposés et un canal de passage (35) disposé entre eux du barillet à pistons radiaux (9) s'alignent les uns sur les autres, de préférence forment un alésage cylindrique traversant avec section transversale constante.
  11. Moteur à pistons radiaux selon une des revendications 1 à 10, caractérisé en ce que respectivement une tête de piston (14') du piston (13') est configurée en forme de coupe en coupe longitudinale et vient reposer de manière étanche par un bord de coupe (63) sans intercaler un élément d'étanchéité séparé sur une surface de gaine intérieure de l'alésage respectif (11) du barillet à pistons radiaux (9), dans lequel les pistons (13') sont de préférence constitués de plastique et de préférence des pièces moulées par injection en plastique.
EP10790918.6A 2009-12-11 2010-12-07 Machine hydrostatique à pistons radiaux Active EP2510192B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009054548A DE102009054548A1 (de) 2009-12-11 2009-12-11 Hydrostatische Radialkolbenmaschine
PCT/EP2010/069078 WO2011070019A1 (fr) 2009-12-11 2010-12-07 Machine hydrostatique à pistons radiaux

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EP2510192A1 EP2510192A1 (fr) 2012-10-17
EP2510192B1 true EP2510192B1 (fr) 2013-06-26

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

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Publication number Priority date Publication date Assignee Title
US9784252B2 (en) 2009-12-11 2017-10-10 Juergen Berbuer Hydrostatic radial piston machine

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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
DE102014215255A1 (de) 2013-08-07 2015-02-12 Schaeffler Technologies Gmbh & Co. Kg 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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US3951044A (en) * 1964-06-11 1976-04-20 Karl Eickmann Rotary radial piston machines with fluidflow supply in substantial axial direction
DE1776238A1 (de) * 1965-05-31 1974-02-28 Breinlich Richard Dr Axial beaufschlagte rotationsfluidmaschine
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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
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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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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9784252B2 (en) 2009-12-11 2017-10-10 Juergen Berbuer Hydrostatic radial piston machine

Also Published As

Publication number Publication date
DE102009054548A1 (de) 2011-06-16
DE202010013078U1 (de) 2011-02-24
CN102652206A (zh) 2012-08-29
US20130145929A1 (en) 2013-06-13
CN102652206B (zh) 2014-12-24
US9784252B2 (en) 2017-10-10
EP2510192A1 (fr) 2012-10-17
WO2011070019A1 (fr) 2011-06-16

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