EP0180912B1 - Machine fluidique à pistons radiaux - Google Patents

Machine fluidique à pistons radiaux Download PDF

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Publication number
EP0180912B1
EP0180912B1 EP85113805A EP85113805A EP0180912B1 EP 0180912 B1 EP0180912 B1 EP 0180912B1 EP 85113805 A EP85113805 A EP 85113805A EP 85113805 A EP85113805 A EP 85113805A EP 0180912 B1 EP0180912 B1 EP 0180912B1
Authority
EP
European Patent Office
Prior art keywords
machine
longitudinal axis
mla
machine according
abutment
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
Application number
EP85113805A
Other languages
German (de)
English (en)
Other versions
EP0180912A2 (fr
EP0180912A3 (en
Inventor
Dieter Schneeweiss
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.)
G Duesterloh GmbH
Original Assignee
G Duesterloh GmbH
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 G Duesterloh GmbH filed Critical G Duesterloh GmbH
Publication of EP0180912A2 publication Critical patent/EP0180912A2/fr
Publication of EP0180912A3 publication Critical patent/EP0180912A3/de
Application granted granted Critical
Publication of EP0180912B1 publication Critical patent/EP0180912B1/fr
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0447—Controlling
    • F03C1/0457—Controlling by changing the effective piston stroke
    • F03C1/046—Controlling by changing the effective piston stroke by changing the excentricity of one element relative to another element
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/12—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members
    • F04B49/123—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element
    • 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
    • F03C1/053—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement the pistons co-operating with an actuated element at the inner ends of the cylinders
    • F03C1/0538—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement the pistons co-operating with an actuated element at the inner ends of the cylinders the piston-driven cams being provided with inlets or outlets
    • 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
    • F04B1/07—Control by varying the relative eccentricity between two members, e.g. a cam and a drive shaft
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2101—Cams
    • Y10T74/2102—Adjustable

Definitions

  • the invention is directed to a fluidic radial piston machine, in particular a hydraulic radial piston machine, according to the features in the preamble of claim 1, see FR-A-2 472119.
  • a radial piston machine belongs to the prior art, which has an eccentric adjustment with hydraulically actuated adjusting pistons provided within the eccentric ring.
  • Such a design has proven itself wherever the eccentric ring could be dimensioned large enough due to the construction volume of the machine to accommodate adjusting pistons with a still satisfactory adjusting force.
  • it can only run reliably in the eccentricity end positions because the adjusting pistons cannot be fixed in intermediate positions. It is therefore a machine that can be switched in two stages.
  • Eccentric adjustments with continuously working adjusting pistons within an eccentric ring are known from DE-PS 26 54 526.
  • additional installation space is required to accommodate double-acting, non-return valves which are arranged in a bearing journal of the machine in the immediate vicinity of the adjusting cylinders.
  • the stepless adjustability with stable intermediate positions is therefore also limited to machine sizes whose volume (displacement volume in a radial piston motor, delivery volume in a radial piston pump) is limited to a minimum of approximately 500 cm 3 .
  • the invention has for its object to develop the hydraulic radial piston machine described in the preamble of claim 1 so that even with comparatively small sizes with a swallowing or delivery volume below about 500 cm 3, a continuous change in the swallowing or delivery volume can be guaranteed.
  • a longitudinal section of the machine shaft is now designed to be pivotable, as is known per se from FR-A-990 841.
  • the pivoting is based on a force-actuated, translationally effective sliding member, the translatory force direction of which is converted into a radial force direction via the swivel arm gear arranged next to the common transverse plane of the working piston.
  • the adjustment mechanism is now next to the row of pistons. Consequently, the support member can now be made very small.
  • the support member shrinks to a size that allows radial piston machines with a swallowing or delivery volume below about 500 cm 3 to be easily adjusted.
  • claim 2 embody an embodiment in which no fixed connection is provided between the swivel link transmission and the hydraulic cylinder which can be acted upon on one side.
  • the hydraulic cylinder therefore does not need to be rotatable. Nevertheless, the return spring in the swivel link mechanism ensures that the swiveling shaft section is shifted into the longitudinal axis of the machine, even when depressurized, so that the swallowing or delivery volume is zero.
  • the inclination of the pivotable shaft section relative to the longitudinal axis of the machine and thus the swallowing or delivery volume can be changed continuously.
  • a fixed connection of the double-acting hydraulic cylinder with the swivel link mechanism is provided.
  • a connection requires a rotatable connection between the hydraulic cylinder and the swivel link transmission.
  • This can e.g. the pivot axis between the piston rod and the compensating link.
  • the piston rod or the piston can also be rotatably supported, if necessary.
  • the piston rod space should always be acted upon by the pressure medium such that the pivotable shaft section is aligned in the longitudinal axis of the machine in the case of unpressurized working cylinders. This can also be brought about by a spring which is provided, for example, in the piston rod space.
  • the support member is arranged to be displaceable parallel to the machine longitudinal axis relative to the working piston. In this way, the fact is taken into account that the space joint between the pivotable shaft section and the support member is inclined Changes the shaft section to the machine longitudinal axis covers an arcuate path that no longer runs in the common transverse plane of the central axes of the working pistons.
  • the pivotable shaft section itself is designed as a sliding member.
  • the telescopic cylinder can be acted upon on one side or on both sides. Since the cylinder housing also carries out a pivoting movement about the articulation point on the axially non-displaceably mounted longitudinal section of the machine shaft, it is necessary to design the support member connected to the cylinder housing in such a way that the working pistons can be supported on the support member in a spatially articulated manner.
  • the support member can have spherical-segment-shaped surfaces on which connecting rod shoes connected in an articulated manner to the working pistons are supported.
  • the support member can also be used in the embodiments as described with reference to claims 2 to 4.
  • a force-actuated, translationally effective sliding member as has been previously described in the scope of a hydraulic cylinder that can be loaded on one or both sides.
  • the rigid or telescopic swivel shaft section penetrates the, for example, disk or plate-shaped abutment in such a way that the abutment can be carried in the sense of rotation, but it is nevertheless ensured that the shaft section in the abutment is the desired one can perform radial relative displacement.
  • the angle between the pivot links is changed and in this way also the angle of inclination of the pivotable shaft section to the longitudinal axis of the machine.
  • the support member is shifted accordingly, thereby changing the swallowing or delivery volume.
  • the swivel link transmission can also have only a single swivel link, which is articulated on the one hand to the abutment and on the other hand to the end of the shaft section which can be pivoted out of the machine longitudinal axis.
  • This embodiment of a swivel link transmission is preferably used, for example, if the pivotable shaft section is designed as a hydraulic cylinder and a further hydraulic cylinder acts as a sliding member on the swivel link transmission, directly or indirectly. It can also be used with advantage if a further pivotable shaft section of a second row of pistons is also struck on the pivoting link. This can be a rigid or telescopic shaft section.
  • a compensating link is provided between the pivot link transmission and the hydraulic cylinder as a sliding member, which compensates for the spatial changes of the pivot link relative to the machine longitudinal axis.
  • the rotating abutment is arranged to be axially displaceable. This can be practiced both in an embodiment with only one row of pistons and in an embodiment with two rows of pistons.
  • the abutment itself forms the sliding link to a certain extent, and the adjusting means for displacing the sliding link can be of a hydraulic, pneumatic, electrical or mechanical nature.
  • the adjusting means for displacing the sliding link can be of a hydraulic, pneumatic, electrical or mechanical nature.
  • this measure can be omitted if one of the shaft sections is designed to be telescopic.
  • Figures 1 to 6 show a schematic representation of various radial piston motors with swivel shaft adjustments.
  • the radial piston engine 1 illustrated in FIG. 1 comprises, for example, five working pistons 2, the central axes of which are arranged in a transverse plane QE common to the machine longitudinal axis MLA.
  • the working pistons 2 slide radially in working cylinders 3. They are supported on a supporting member 4, which is displaceable relative to the working pistons 2 parallel to the longitudinal axis MLA of the machine.
  • the support member 4 is radial via a space joint 5 with one from the machine longitudinal axis MLA pivotable rigid shaft section 6 connected.
  • the end 9 of the pivotable shaft section 6 opening into the machine longitudinal axis MLA is hinged in space-related fashion to a longitudinal section 7 of the machine shaft 8 which rotates about the machine longitudinal axis M LA but is axially immovable.
  • the slot-like bushing 11 in the abutment 12 for the shaft section 6 is dimensioned such that the abutment 12 can be taken along by the shaft section 6 in the correct direction of rotation and the shaft section 6 can be radially displaced in the slot 11.
  • the pivot axis 15 runs at a distance from the machine longitudinal axis MLA and perpendicular to this.
  • the swivel link transmission 14 comprises a further swivel link 16 which is articulated on the one hand to a bracket 17 connected to the abutment 12 and on the other hand to the swivel link 13.
  • Both the swivel axis 18 between the two swivel arms 13 and 16 and the swivel axis 19 between the bracket 17 and the swivel arm 16 extend next to the machine longitudinal axis MLA and perpendicular to it.
  • a slider 20 is also articulated to the pivot axis 18 and is under the influence of a spring 21 arranged between the abutment 12 and the pivot axis 18.
  • the slider 20 is supported in an unconnected manner on a plunger 22 of a hydraulic cylinder 23 which can be acted upon on one side and whose longitudinal axis 24 coincides with the machine longitudinal axis MLA.
  • the return spring 21 presses the plunger 22 into the cylinder housing 25 and thus also shifts the shaft section 6 into the machine longitudinal axis MLA.
  • the swallowing volume is then zero.
  • the plunger 22 can now be pushed out, the pivotable shaft section 6 and thereby also the support member 4 being radially displaced via the slide 20 and the swivel link mechanism 14. In this way, the swallowing volume of the radial piston motor 1 can be varied continuously.
  • the hydraulic cylinder 23 which can be acted on on one side has been replaced by a hydraulic cylinder 26 which can be acted on on both sides.
  • the hydraulic cylinder 26 comprises a piston 27 with a piston rod 28, which is articulated via a compensating link 29 to a swivel link transmission 14 according to FIG. 1.
  • the other components of this embodiment are designed in accordance with the embodiment of FIG. 1. A further explanation is therefore unnecessary.
  • the hydraulic cylinder 26 Due to the direct connection of the hydraulic cylinder 26 to the swivel link mechanism 14, however, it is necessary, for example, to mount the piston rod 28 or the piston 27 of the hydraulic cylinder 26 such that they can rotate. Such a connection can also be provided in the pivot axis 30 between the piston rod 28 and the compensating link 29.
  • a compression spring 32 it may be expedient to arrange a compression spring 32 in the piston rod space 31. This compression spring 32 has the purpose of displacing the pivotable shaft section 6 back into the machine longitudinal axis MLA when the radial piston motor 1 'is depressurized. However, this measure can also be carried out by correspondingly pressurizing the piston rod chamber 31.
  • the compensating link 29 can be used as a variable unbalance compensating member.
  • the pivotable shaft section is designed as a hydraulically actuatable telescopic cylinder 33.
  • the telescopic cylinder 33 can be acted on on one side or on both sides Conrod shoes 36, which are articulated to the working piston 2.
  • the end 9 of the shaft section 6 opening into the machine longitudinal axis MLA is connected in a spatially articulated manner to the axially immovable length section 7 of the machine shaft 8 rotating in the machine longitudinal axis MLA.
  • the telescopic longitudinal section 37 of the telescopic cylinder 33 passes through a disk-like abutment 38 which rotates about the machine longitudinal axis MLA, but is mounted immovably in the direction of the machine longitudinal axis MLA.
  • the abutment 38 has a slot 39, through which the telescopic part 37 passes so that the abutment 38 is carried along in the direction of rotation and the telescopic part 37 can be displaced radially.
  • the abutment 38 forms part of a swivel arm gear 40 which has a swivel arm 41 which is connected on the one hand via a swivel axis 42 to a bracket 43 connected to the abutment 38 and on the other hand via a swivel axis 44 to the telescopic part 37 of the telescopic cylinder 33.
  • Both pivot axes 42 and 44 extend laterally next to the machine longitudinal axis M LA and perpendicular to it.
  • a bracket 45 is fastened approximately in the middle of the swivel arm 41, to which a compensating arm is attached 46 is articulated.
  • the other end section of the compensating link 46 is articulated via a joint 30 to a piston rod 28 of a hydraulic cylinder 26, as has been described, for example, with reference to FIG. 2.
  • the hydraulic cylinder 26 forming the sliding member can also be acted upon mechanically by a spring 32 in the piston rod space 31 or hydraulically in the piston rod space 31 or, if appropriate, also in the piston space 47.
  • FIG. 4 shows an embodiment of a radial piston motor 1 '"with two rows of working pistons 2.
  • An arrangement of the adjustment as shown in FIG. 3 is selected, but with the exception of the hydraulic cylinder 26.
  • This is in the embodiment of the figure 4 can be dispensed with, since the inclination of the telescopic cylinder 33 towards the longitudinal axis MLA of the machine can be changed via the swivel link mechanism 40 and thus the swallowing volume by appropriate loading.
  • FIG. 5 shows a radial piston motor 1 "" with a rigid pivotable shaft section 6 and a row of pistons according to the embodiments of FIGS. 1 and 2.
  • the end 10 of the shaft section 6 which is pivotable from the machine longitudinal axis MLA is coupled to a swivel arm gear 40, as has been explained with reference to FIG. 3.
  • the difference is further that the abutment 38 is now axially displaceable.
  • the actuating means required for this can be of a hydraulic, pneumatic, electrical or mechanical nature. It can be seen that by adjusting the abutment 38 parallel to the machine longitudinal axis M LA in the operating position with broken lines, the inclination of the pivotable shaft section 6 to the machine longitudinal axis MLA and thus the displacement volume of the radial piston motor 1 "" can be changed.

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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)

Claims (10)

1. Machine fluidique à pistons radiaux, notamment machine hydraulique à postons radiaux dont on peut faire varier le volume en continu et dans laquelle les pistons de travail agencés avec leurs axes médians dans un plan transversal commun par rapport à l'axe longitudinal de la machine viennent en appui de façon coulissante au moins indirectement sur un élément d'appui relié à l'arbre de la machine, déplaçable radialement par rapport à l'arbre de la machine, caractérisée en ce que la section longitudinale (6, 33) de l'arbre de la machine (8) traversant le plan transverale commun (QE) des pistons de travail (2) peut basculer à partir de l'axe longitudinal (M LA) de la machine (1, 1', 1 ", 1 "', 1 "", 1 ""') et elle est reliée de façon articulée dans l'espace à l'élément d'appui (4, 35) mobile relativement aux pistons de travail (2), moyennant quoi l'extrémité (9) aboutissant dans l'axe longitudinal de la machine (MLA) de la section d'arbre pivotante (6, 33) est fixée de façon articulée dans l'espace sur la section longitudinale (7) non déplaçable axialement de l'arbre de la machine (8), section longitudinale (7) tournant autour de l'axe longitudinal de la machine et l'extrémité (10,37) déplaçable radialement à partir de l'axe longitudinal de la machine (MLA), de la section d'arbre (6, 33) est accouplée par incorporation d'un élément coulissant actif par translation, soumis à une force, à un mécanisme d'orientation (14,40) monté de façon pivotante à proximité du plan transversale (QE) autour de l'axe lontitudinal de la machine (MLA) avec des axes pivotants (15, 18,19: 42, 44) se déplaçant perpendiculairement à l'axe longitudinal de la machine (MLA) de façon à pouvoir être entrainé dans le sens de rotation.
2. Machine à pistons radiaux selon la revendication 1, caractérisée en ce que l'élément coulissant consiste en un vérin hydraulique pouvant être actionné d'un côté (23), dont l'axe longitudinal (24) coïncide avec l'axe longitudinal de la machine (MLA) et dont la partie mobile axialement (22) repose sur un élément coulissant (20) déplaçable en opposition à la force de rappel élastique d'un ressort (21), élément coulissant qui est relié au mécanisme d'orientation (14) de façon articulée.
3. Machine à pistons radiaux selon la revendication 1, caractérisée en ce que l'élément coulissant consiste en un vérin hydraulique (26) actionnable des deux côtés, dont l'axe longitudinal coïncide avec l'axe longitudinal de la machine (MLA) et dont la tige de piston (28) est reliée via une biellette de compensation (29, 46) au mécanisme d'orientation (14,40).
4. Machine à pistons radiaux selon l'une quelconque des revendications 1 à 3, caractérisé en ce que la section d'arbre pivotante (6) est conçue de façon rigide sur la totalité de sa longueur et l'élément d'appui (4) relié de façon articulée dans l'espace avec celle-ci peut se déplacer parallèlement à l'axe longitudinal de la machine (MLA).
5. Machine à pistons radiaux selon l'une quelconque des revendications 1 à 3, caractérisée en ce que la section d'arbre pivotante est conçue en tant que vérin télescopique (33) actionnable hydrauliquement dont le logement (34) supporte l'élément d'appui (35) sur lequel reposent les pistons de travail (2) de façon articulée dans l'espace.
6. Machine à pistons radiaux selon l'une quelconque des revendications 1 à 3, caractérisée en ce que le mécanisme d'orientation (14) comporte une butée (12) immobile axialement, rotative parallèlement au plan tranversal (QE) autour de l'axe longitudinal de la machine (MLA) et pouvant être entraînée par la section d'arbre pivotante (6) dans le sens de rotation ainsi que déplaçable radialement de façon relative, butée sur la quelle est articulée dans l'espacement radial à partir de l'axe longitudinal de la machine (MLA) une biellette pivotante (16), laquelle est reliée de façon articulée aussi bien à une autre biellette pivotante (13) fixée de façon articulée sur l'extrémité (10) de la section d'arbre (6) avec l'élément coulissant (20), qu'avec la biellette de compensation (29).
7. Machine à pistons radiaux selon l'une quelconque des revendications 1 à 3, caractérisée en ce que le mécanisme d'orientation (40) présente une butée (38) parallèlement au plan transversal (QE) rotatif autour de l'axe longitudinal de la machine (MLA) et pouvant être entraînée dans le sens de rotation par la section d'arbre pivotante (6, 33) et pouvant être déplacée radialement de façon relative, sur laquelle est fixée une biellette pivotante (41 ) montée de façon articulée avec l'autre extrémité sur au moins une section d'arbre (6,33) pivotante.
8. Machine à pistons radiaux selon la revendication 7, caractérisée en ce que dans la zone longitudinale médiane la biellette pivotant (41 ) est articulée, une biellette de compensation (46) reliée de façon articulée également avec la tige de piston (28) d'un vérin hydraulique (26) pouvant être actionné au moins sur le côté de la tige de piston.
9. Machine à pistons radiaux selon la revendication 7, caractérisée en ce que la butée rotative (12, 38) est montée de façon immobile axialement.
10. Machine à pistons radiaux selon la revendications 7, caractérisée en ce que la butée rotative (38) est montée de façon immobile axialement et soumise à l'influence de moyens de commande.
EP85113805A 1984-11-07 1985-10-30 Machine fluidique à pistons radiaux Expired EP0180912B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3440543A DE3440543A1 (de) 1984-11-07 1984-11-07 Fluidische radialkolbenmaschine
DE3440543 1984-11-07

Publications (3)

Publication Number Publication Date
EP0180912A2 EP0180912A2 (fr) 1986-05-14
EP0180912A3 EP0180912A3 (en) 1987-04-15
EP0180912B1 true EP0180912B1 (fr) 1989-04-12

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP85113805A Expired EP0180912B1 (fr) 1984-11-07 1985-10-30 Machine fluidique à pistons radiaux

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US (1) US4768421A (fr)
EP (1) EP0180912B1 (fr)
DE (1) DE3440543A1 (fr)

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DE4122486A1 (de) * 1991-07-06 1993-01-07 Teves Gmbh Alfred Antriebsaggregat, insbesondere motor-pumpenaggregat fuer schlupfgeregelte bremsanlagen
DE10208586A1 (de) 2002-02-22 2003-09-11 Reinhard Sorg Antriebseinrichtung für eine Maschine, insbesondere Pumpe oder Motor
JP4813367B2 (ja) * 2003-12-15 2011-11-09 ハイドロスタティック デザイン テクノロジー ピー・ティー・ワイ リミテッド 液圧モータ／ポンプ
US8413572B1 (en) 2006-11-22 2013-04-09 Westendorf Manufacturing, Co. Auto attachment coupler with abductor valve
FR2981703B1 (fr) * 2011-10-21 2013-11-22 Hydr Am Pompe hydraulique radiale a excentricite et debit variables

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Also Published As

Publication number Publication date
EP0180912A2 (fr) 1986-05-14
DE3440543C2 (fr) 1989-05-03
DE3440543A1 (de) 1986-05-22
US4768421A (en) 1988-09-06
EP0180912A3 (en) 1987-04-15

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