EP0401408B1 - Machine à pistons radiaux - Google Patents

Machine à pistons radiaux Download PDF

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Publication number
EP0401408B1
EP0401408B1 EP89110348A EP89110348A EP0401408B1 EP 0401408 B1 EP0401408 B1 EP 0401408B1 EP 89110348 A EP89110348 A EP 89110348A EP 89110348 A EP89110348 A EP 89110348A EP 0401408 B1 EP0401408 B1 EP 0401408B1
Authority
EP
European Patent Office
Prior art keywords
piston
radial
cylinder
engine according
ring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP89110348A
Other languages
German (de)
English (en)
Other versions
EP0401408A1 (fr
Inventor
Jürgen Dr.-Ing. Berbuer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
LuK Fahrzeug Hydraulik GmbH and Co KG
Original Assignee
LuK Fahrzeug Hydraulik GmbH and Co KG
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 LuK Fahrzeug Hydraulik GmbH and Co KG filed Critical LuK Fahrzeug Hydraulik GmbH and Co KG
Priority to DE89110348T priority Critical patent/DE58906590D1/de
Priority to EP89110348A priority patent/EP0401408B1/fr
Priority to US07/534,674 priority patent/US5079994A/en
Priority to JP2148840A priority patent/JPH086682B2/ja
Publication of EP0401408A1 publication Critical patent/EP0401408A1/fr
Application granted granted Critical
Publication of EP0401408B1 publication Critical patent/EP0401408B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F04B1/10—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
    • F04B1/0404—Details or component parts
    • F04B1/0408—Pistons

Definitions

  • the invention relates to a radial piston machine, in particular a radial piston pump for automobiles.
  • a radial piston machine of the type mentioned here is known from US Pat. No. 3,087,437. It has a cylindrical star with radial cylinder bores, in each of which a one-piece piston is pivotably guided. This comprises a spherical piston head, a piston neck and a piston shoe cooperating with a cam ring arranged eccentrically to the cylinder star. It has been shown that the piston heads are exposed to high wear during operation of the radial piston machine, since the conversion between hydraulic pressure and torque takes place by means of tangential forces due to between the piston and the wall of the cylinder bore.
  • a radial piston machine with the features mentioned in the preamble of claim 1 is also known from German Offenlegungsschrift DE-A 24 60 512.
  • a cylinder star with cylinder bores is also provided here, in each of which a one-piece piston is guided.
  • Another radial piston machine is known from British Patent GB-A-1 468 658, which in turn has a cylinder star with cylinder bores, in each of which a one-piece piston is pivotally guided.
  • a special feature of the radial piston machine is that the pistons are inclined when the cylinder star rotates.
  • the piston head is provided with a piston groove receiving a piston ring, the rim facing the piston neck at the largest diameter of the piston head is arranged, wherein the piston ring has a conical-spherical outer surface, there is a line seal between the piston ring and the inner wall of the cylinder bore receiving the piston.
  • the sealing line is tilted with respect to the central axis of this bore, so that there are wall regions of different sizes within the cylinder bore, to which the pressure of the fluid flowing through the radial piston machine acts.
  • the largest inclination angle ⁇ occurs at a piston position of 90 ° if the zero position in the main eccentricity plane is assumed.
  • a line seal by means of a piston ring is preferred, which is between the changing shape Can adjust the ellipse and circle and does not lead to excessive edge pressures.
  • the piston ring groove with its neck-side edge is arranged on the largest diameter of the piston head and the piston ring is equipped with a conical-spherical outer surface.
  • the basic shape of the piston ring is therefore conical, with the piston ring being revised crowned at the largest diameter.
  • the length of the respective cylinder bore is only slightly greater than the stroke of the associated piston. Furthermore, the supply and discharge of the fluid can take place in a space-saving manner through the centrally arranged control mirror pin, that is, one can avoid inflow and outflow channels in radially outer housing parts.
  • the manufacture is inexpensive insofar as it is essentially a matter of rotationally symmetrical components, the pistons have a simple design and there are also no high demands on the manufacturing accuracy of the cylinder bores.
  • the piston shoe which is preferably made in one piece with the piston neck and the piston head, has a cylindrical support surface in order to be in contact with the Support the inner race of the cam ring.
  • the cylindrical wing is connected asymmetrically above the piston neck to the piston head, the front wing part in the running direction being larger than the rear wing part. If the wings of the piston shoes are lubricated from the respective pump chamber via a hole in the piston, a symmetrical arrangement of the piston shoe and piston head can also be carried out. This type of lubrication also leads to hydrostatic relief of the pistons.
  • the fluid enclosed between the separator and the cylinder space can be pre-compressed before it is connected to the actual pressure space. If the pre-compression at the time of connection corresponds exactly to the pressure in the pressure chamber, there is no structure-borne noise excitation. Therefore, the separator between low pressure and high pressure is widened in the direction of rotation of the pump by an amount ⁇ that is suitable for producing a suitable pre-compression of the enclosed pressure fluid. Adjustments to different operating pressures can be made using pilot control notches.
  • the radial piston machine is designed with a variable displacement volume, this means that the respective piston strokes are reduced and thus the achievable pre-compression pressure is also reduced with a decreasing displacement volume.
  • the stroke ring of the radial piston machine is adjusted tangentially along a specially aligned guide, as a result of which the eccentricity of the stroke ring is spatially aligned in a certain way, which is noticeable like an adjustment of the lead angle between the pump star and the control pin.
  • the cam ring is tangential along a guide by a first amount of eccentricity adjustable, and the vertical distance of the guide from the axis of rotation of the cylinder star is smaller by a second amount of eccentricity than the diameter of the cam ring.
  • the novel radial piston machine can be constructed with one or more disks, i. H. two or more cylinder stars arranged next to one another can be provided, which run on the same control mirror journal and are connected to one another via entrainment means.
  • a control mirror pin 2 is inserted in a sealed manner in a housing 1.
  • Inlet channels 3 and outlet channels 4 each lead to inlet grooves 5 and outlet grooves 6.
  • the grooves 5 and 6 are separated from one another by separating webs 7 and 8.
  • the control mirror pin 2 also has a central bore 9 through which a shaft 10 is passed in order to drive a further unit, not shown.
  • the shaft 10 is supported by bearings 11 in the housing 1 and drives a drive disk 12 via a spline 13 or the like.
  • the drive pulley 12 is connected to a cylindrical star 14, which is provided with a number of radially extending cylinder bores 15, which are each provided with a passage opening 17 on their base 16.
  • the number of cylinder bores 15 can be freely selected within a certain range, i. H. both even and odd numbered cylinders can be used.
  • a one-piece piston 20 is guided, which has a spherical piston head 21, a piston groove 22, a piston neck 23 and one Piston shoe 24 has.
  • the groove 22 is made along the largest diameter of the spherical piston head 21, namely the neck-side edge of the piston groove 22 coincides with the equator of the piston head 21.
  • the piston shoe 24 has a rectangular outline and a cylindrical wing, in which a front wing part 25 and a rear wing part 26 can be distinguished. The areas of these two wing parts are 58 and 42%, respectively.
  • the shoe 24 is connected asymmetrically to the piston neck 23 and piston head 21. This design is used for hydrodynamic lubrication since the lift on the rear wing part 26 is somewhat greater than on the front wing part 25.
  • the wing parts 25 and 26 can also be arranged symmetrically, as shown in FIGS. 5 and 6, which is particularly considered when a lubrication channel 27 leads from the pump chamber 17 to the wings 25, 26.
  • the wing parts 25, 26 can also be interrupted by an annular groove 28 which delimit a surface corresponding to the head 21 and are connected via a relief bore 29 with low pressure in order to provide hydrostatic relief.
  • a slotted piston ring 30 is inserted in the piston groove 22, the slot 31 of which can be seen in FIG. 2 and which enables a certain elastic change in shape of the piston ring 30, which is necessary because the piston head 21 can be inclined in the cylinder bore 15.
  • the piston ring 30 must therefore temporarily change from the circular shape to a weak elliptical shape, which also leads to displacements and swivels of the outer piston ring surface 32 to the cylinder wall.
  • the fluid pressure acts on the piston ring 30 from the outside and also from the inside, the piston groove 22, forth and in order to balance the fluid pressure on the piston ring, a trapezoidal cross-sectional shape of the piston ring 30 would be preferred.
  • the piston ring 30 is designed spherical in the region of its largest diameter 33, as can best be seen from FIG. 7 at 34.
  • the crowning radius can also be continued up to the smaller diameter of the piston ring.
  • the piston shoes 24 work together with a cam ring 35 (FIGS. 1 and 2) which has an inner running surface 36 and an outer surface 37.
  • the inner running surface 36 is arranged eccentrically to the cylinder star 14 and therefore transmits a stroke movement to the pistons 20 when the cylinder star rotates.
  • the return stroke is provided by hold-down rings 38 which engage on the inside of the piston shoes 24 in edge grooves formed there, so that overall positive guidance is achieved becomes.
  • the pump chamber 18 enclosed between the piston head 20 and the cylinder bore 15 widens at the inlet grooves 5 and narrows at the outlet grooves 6. As a result, the fluid is sucked in on the side 5 and displaced on the side 6, which results in the pump flow.
  • the separating webs 7 and 8 are each wider than the passage openings 17, namely that widening points in the angular range ⁇ are offset at least in each case in the direction of rotation of the cylindrical star 14. Accordingly, if the pumping spaces 18 move over the web 7 during their circulation, then the piston 20 already begins to compress the enclosed fluid before it comes into contact with the groove 6, in which the high pressure prevails. If this pre-compression corresponds exactly to the fluid pressure in the groove 6, there is no pressure release and thus no sound excitation. The aim is therefore to design the amount of pre-compression so that it corresponds to the desired pump pressure. Deviations can be compensated for by pre-tax notches in the range ⁇ as long as these deviations are not too large.
  • the dividers 7, 8 can also be arranged symmetrically to the plane 40-40, the widening points then being on both sides.
  • the radial piston pump described can also be designed as a control pump, as shown in FIG. 2.
  • the actuating system acts along an actuating plane 40 and has a small cylinder 41 with a small actuating piston 42 and a large actuating cylinder 43 with a large actuating piston 44 and a spring 45.
  • the small actuating piston 42 is constantly pressurized with the pump pressure and the large actuating piston 44 with control pressure which is less than the pump pressure. It can be regulated to a constant delivery volume or to a constant delivery pressure, which need not be described further. In general, however, this leads to adjusting movements of the cam ring 35 and thus to changed eccentricities e and changed pre-compression amounts, which would thus be mismatched with the system.
  • the radial piston pump can also be designed for two or more cylinder stars 14.
  • the individual cylinder stars are coupled with one another in their rotational movement via driving claws 48 or the like, while a certain radial displacement between the cylinder stars remains possible.
  • two common suction connections 3 are provided, while the pressure connections 4a, 4b are separated for the two pump disks.
  • the bushing 9 is not absolutely required for the shaft 10 and this space could also be used for fluid channels.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)

Claims (8)

  1. Machine à pistons radiaux, en particulier pompe à pistons radiaux pour automobiles, présentant les caractéristiques suivantes :
       une culasse de commande (2) est pourvue de canaux d'entrée et de sortie (3, 4) conduisant à des rainures d'entrée et de sortie correspondantes (5, 6) qui sont séparées les unes des autres par des parois de séparation (7, 8) et qui sont destinées au fluide traversant la machine ;
       un bloc de cylindres en étoile (14) est monté tournant par rapport à la culasse de commande (2), et il contient une pluralité d'alésages (15) présentant chacun un orifice de passage (17) qui coopère avec la rainure d'entrée (5), avec la rainure de sortie (6) ou avec l'une des parois de séparation (7, 8), selon la position en rotation du bloc de cylindres en étoile ;
       dans chaque alésage (15) est guidé en pivotement un piston d'un seul tenant (20) qui comporte une tête de piston sphérique (21) une gorge de piston (22) et au moins un segment de piston (30) qui est inséré dans celle-ci, un col de piston (23) et une semelle de piston (24) coopérant avec une couronne de glissement (35) disposée d'une manière excentrée par rapport au bloc de cylindres en étoile (14), la longueur totale du piston (20) étant choisie de manière à être supérieure à la longueur de l'alésage associé (15) ;
       lors de la rotation du bloc de cylindres en étoile, la couronne de glissement (35) imprime un déplacement aux pistons (20), de sorte que les pistons (20) s'inclinent d'un certain angle (α) et que la chambre de pompage (18) comprise entre la tête (21) du piston et l'alésage (15) devient plus grande sur les rainures d'entrée (5) et devient plus petite sur les rainures de sortie (6),
       caractérisée par le fait que la gorge (22) du piston est disposée sur le plus grand diamètre de la tête (21) du piston par son bord qui est situé du côté du col, et par le fait que le segment de piston (30) présente une surface extérieure (32) en forme de cône arrondi.
  2. Machine à pistons radiaux selon la revendication 1, caractérisée par le fait que la longueur totale d'un piston (20) est choisie de manière à être seulement un peu plus grande que la longueur d'un alésage associé (15).
  3. Machine à pistons radiaux selon la revendication 1 ou 2, caractérisée par le fait que l'excentricité de la couronne de glissement (35) est limitée à une valeur qui conduit à un maximum de 10° pour l'angle d'inclinaison (α) des pistons (20).
  4. Machine à pistons radiaux selon la revendication 3, caractérisée par le fait que le maximum de l'angle d'inclinaison (α) est à peu près égal à 7,75°.
  5. Machine à pistons radiaux selon l'une des revendications 1 à 4, caractérisée par le fait que la semelle (24) du piston présente une surface porteuse cylindrique (25, 26) qui est reliée à la tête (21) du piston d'une manière asymétrique par l'intermédiaire du col (23) du piston, la partie (25) de la surface porteuse qui est à l'avant dans la direction de marche étant plus grande que la partie arrière (26) de la surface porteuse.
  6. Machine à pistons radiaux selon l'une des revendications 1 à 5, caractérisée par le fait que la surface porteuse (25, 26) de la semelle (24) du piston est reliée à la chambre de pompage associée (18) par l'intermédiaire d'un canal (27).
  7. Machine à pistons radiaux selon l'une des revendications 1 à 6, caractérisée par le fait que les parois de séparation (7, 8) sont élargies d'une valeur (τ).
  8. Machine à pistons radiaux selon l'une des revendications 1 à 7, comprenant deux ou plusieurs blocs de cylindres en étoile juxtaposés (14) qui se déplacent sur la même culasse de commande (2) et qui sont reliés entre eux par l'intermédiaire de moyens d'entraînement (48).
EP89110348A 1989-06-08 1989-06-08 Machine à pistons radiaux Expired - Lifetime EP0401408B1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
DE89110348T DE58906590D1 (de) 1989-06-08 1989-06-08 Radialkolbenmaschine.
EP89110348A EP0401408B1 (fr) 1989-06-08 1989-06-08 Machine à pistons radiaux
US07/534,674 US5079994A (en) 1989-06-08 1990-06-07 Radial piston machine
JP2148840A JPH086682B2 (ja) 1989-06-08 1990-06-08 ラジアルピストン装置

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP89110348A EP0401408B1 (fr) 1989-06-08 1989-06-08 Machine à pistons radiaux

Publications (2)

Publication Number Publication Date
EP0401408A1 EP0401408A1 (fr) 1990-12-12
EP0401408B1 true EP0401408B1 (fr) 1993-12-29

Family

ID=8201475

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89110348A Expired - Lifetime EP0401408B1 (fr) 1989-06-08 1989-06-08 Machine à pistons radiaux

Country Status (4)

Country Link
US (1) US5079994A (fr)
EP (1) EP0401408B1 (fr)
JP (1) JPH086682B2 (fr)
DE (1) DE58906590D1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019205824A1 (de) * 2019-04-24 2020-10-29 Zf Friedrichshafen Ag Pumpe, insbesondere Ölpumpe für ein Getriebe

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07317652A (ja) * 1994-05-25 1995-12-05 Sumitomo Electric Ind Ltd プランジャ式ポンプ
GB9525028D0 (en) * 1995-12-06 1996-02-07 Unipat Ag Hydrostatic piston machine
ITMO20040165A1 (it) * 2004-06-30 2004-09-30 Apparecchiature Idrauliche S P Macchina a fluido con cilindri radiali perfezionata.
US7484939B2 (en) * 2004-12-17 2009-02-03 Eaton Corporation Variable displacement radial piston pump
EP2206937B1 (fr) * 2009-01-13 2013-06-05 Sauer-Danfoss ApS Améliorations de ou associées aux segments de piston
BRPI0919988A2 (pt) 2009-01-20 2018-10-23 Eaton Corp conjunto de deslocamento variável e dispositivo de fluido
DE102009054548A1 (de) 2009-12-11 2011-06-16 Berbuer, Jürgen, Dr.-Ing. Hydrostatische Radialkolbenmaschine
US9399984B2 (en) * 2012-06-25 2016-07-26 Bell Helicopter Textron Inc. Variable radial fluid device with counteracting cams
US9228571B2 (en) * 2012-06-25 2016-01-05 Bell Helicopter Textron Inc. Variable radial fluid device with differential piston control
DE102014215255A1 (de) 2013-08-07 2015-02-12 Schaeffler Technologies Gmbh & Co. Kg Radialkolbenmaschine
US10683854B2 (en) * 2015-05-21 2020-06-16 Eaton Intelligent Power Limited Radial piston device with reduced pressure drop
JP6321700B2 (ja) * 2016-02-26 2018-05-09 三菱重工業株式会社 油圧機械および風力発電装置
DE102019116680A1 (de) * 2019-06-19 2020-12-24 Moog Gmbh Radialkolbenmaschine mit einem Kugelkolben
CN112177843B (zh) * 2020-10-09 2023-05-16 东莞市普林斯机电设备有限公司 一种内曲线径向柱塞液压马达
CN112253374B (zh) * 2020-10-09 2023-12-12 宁波真格液压科技有限公司 一种变量液压马达
CN112112753A (zh) * 2020-10-09 2020-12-22 段井胜 一种液压马达
KR102534467B1 (ko) * 2023-01-02 2023-05-30 하이드로텍(주) 다단 레이디얼 피스톤 펌프

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB524384A (en) * 1938-12-21 1940-08-06 Aircraft Hydraulic Appliances Improvements in radial pumps
US3084633A (en) * 1957-09-09 1963-04-09 North American Aviation Inc Hydraulic pump or motor
DE1243520B (de) * 1958-09-04 1967-06-29 North American Aviation Inc Schmiereinrichtung an einem innenbeaufschlagten mehrteiligen Kolben einer Radialkolbenmaschine
US3087437A (en) * 1959-10-12 1963-04-30 North American Aviation Inc High temperature variable displacement pump
US3357362A (en) * 1966-06-17 1967-12-12 Allis Chalmers Mfg Co Hydrostatic power unit
AT331639B (de) * 1972-01-07 1976-08-25 Eickmann Karl Radialkolben-maschine, insbesondere pumpe oder motor, mit rotierendem zylinderblock
GB1468658A (en) * 1974-03-06 1977-03-30 Lucas Ltd Piston for use in a radial piston pump or motor
DE2460512A1 (de) * 1974-12-20 1976-06-24 Linde Ag Radialkolbenmaschine
JPS5559172U (fr) * 1978-10-16 1980-04-22
CH638590A5 (de) * 1979-02-26 1983-09-30 Sulzer Ag Hydrostatische kolbenmaschine.
JPS5999074A (ja) * 1982-11-29 1984-06-07 Hitachi Constr Mach Co Ltd ラジアルピストン式液圧回転機
JP2521481B2 (ja) * 1987-07-03 1996-08-07 川崎重工業株式会社 液圧ピストンポンプ・モ−タ
US4848213A (en) * 1988-01-11 1989-07-18 The Devilbiss Company Reciprocating piston compressor with offset cylinder

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019205824A1 (de) * 2019-04-24 2020-10-29 Zf Friedrichshafen Ag Pumpe, insbesondere Ölpumpe für ein Getriebe

Also Published As

Publication number Publication date
EP0401408A1 (fr) 1990-12-12
JPH03115782A (ja) 1991-05-16
DE58906590D1 (de) 1994-02-10
JPH086682B2 (ja) 1996-01-29
US5079994A (en) 1992-01-14

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