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EP1062426A2 - Moteur a pistons radiaux avec guidage des galets - Google Patents

Moteur a pistons radiaux avec guidage des galets

Info

Publication number
EP1062426A2
EP1062426A2 EP99915563A EP99915563A EP1062426A2 EP 1062426 A2 EP1062426 A2 EP 1062426A2 EP 99915563 A EP99915563 A EP 99915563A EP 99915563 A EP99915563 A EP 99915563A EP 1062426 A2 EP1062426 A2 EP 1062426A2
Authority
EP
European Patent Office
Prior art keywords
roller
cylinder
piston
rotation
axis
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.)
Granted
Application number
EP99915563A
Other languages
German (de)
English (en)
Other versions
EP1062426B1 (fr
Inventor
Sinclair Cunningham
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.)
Bosch Rexroth AG
Original Assignee
Mannesmann Rexroth AG
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 Mannesmann Rexroth AG filed Critical Mannesmann Rexroth AG
Publication of EP1062426A2 publication Critical patent/EP1062426A2/fr
Application granted granted Critical
Publication of EP1062426B1 publication Critical patent/EP1062426B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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
    • F04B1/0404—Details or component parts
    • F04B1/0439—Supporting or guiding means for the pistons
    • 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
    • F03C1/0428—Supporting and guiding means for the pistons
    • 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 present invention relates to a radial piston motor with roller guides for axially guiding the rollers, by means of which the pistons are supported on the cam ring.
  • a radial piston motor corresponding to the preamble of claim 1 is known, which was based on the task of reducing the manufacturing outlay previously associated with the axial positioning of the rollers and thus reducing the manufacturing and assembly costs.
  • This object should be achieved in that in the spaces between the end faces of the rollers and the inner surface of the cylinder a wedge piece with a circular segment-like cross section, viewed in the stroke direction of the piston, is arranged as a roller guide, which axially positions the roller relative to the cam ring in the cylinder.
  • the wedge pieces disclosed in the above-mentioned document can essentially be divided into three different types.
  • each wedge piece on the side facing the roller has a flat surface resting on the end face of the roller and on the side facing away from the roller has a cylindrical surface contacting the inner surface of the cylinder.
  • this wedge piece is accommodated in the space between the roller, piston and inner surface of the cylinder without being permanently connected to any of these components. Because of this arrangement of the wedge piece relative to the roller, which is freely movable in the piston stroke direction, the piston takes the wedge pieces in the direction of the lifting ring during a load stroke. There is still no contact between the wedge pieces and the cams formed on the cam ring. On the other hand, during the subsequent idle stroke of the piston, the wedge pieces hit the cams formed on the cam ring.
  • one of the two wedge pieces on the side facing the cylinder inner surface has an elongated groove into which a screw, clamp or the like which passes through the cylinder wall engages and in this way, a rotation of the piston in the cylinder and thus the roller against the cam ring is prevented.
  • the formation of the groove causes a weakening of the wedge piece in question and thus a shortening of the service life of the wedge piece which is heavily stressed during operation of the radial piston motor.
  • the sliding contact between the wedge piece and the screw or clamp takes place, which appears disadvantageous with regard to good roller guidance.
  • such a constructive measure means a high manufacturing effort.
  • the object of the present invention is therefore to create a technically optimized radial piston motor which is characterized by a low manufacturing outlay and, at the same time, reliable operation.
  • roller guides arranged on the end faces of the rollers are connected to the respective roller so as to be non-displaceable in the piston stroke direction.
  • the roller guides are carried along by the respective roller in the piston stroke direction, ie both during the load stroke and during the empty stroke, the roller guides can be dimensioned such that they do not protrude beyond the outer circumference of the respective roller, so that between there is no butt contact between the roller guides and the cam ring. Ultimately, this leads to an increase in the service life of the roller guides and thus to reliable operation of the radial piston motor as a whole. In addition, material is saved in the manufacture of the roller guides. If the roller guides do not come into contact with the cam ring, the width of the cam ring can furthermore be reduced to a width which corresponds at most to the width of the rollers. In this way, apart from the total weight of the radial piston motor, the manufacturing outlay and thus the manufacturing costs with regard to precision machining of the stroke curve of the stroke ring are considerably reduced.
  • roller guides which is displaceable in the stroke direction can be implemented by means of simple production-related measures.
  • the roller guides can have a cylindrical projection which can be inserted into a central, cylindrical recess formed on the front side of the roller.
  • the roller guides can have a recess on the side facing the end of the roller, into which a projection formed on the end of the roller can be inserted.
  • the recess and the projection which engages with the recess could also be conical.
  • the diameters of the recesses and the protrusions are dimensioned such that they are small compared to the outer diameter of the roller, that is to say that the protrusions and the recesses concentrate on a central region around the axis of rotation of the roller, and the protrusions stand in the manner with the respective ones Engages recesses that between between the ring surface of the roller around the recess and the surface around the projection of the roller guide, the peripheral speeds present on the outer circumference of the projection and on the inner peripheral wall of the recess and thus the relative speed between the roller and roller guides decrease during operation of the radial piston motor .
  • since there is no friction on the two spaced-apart surfaces of the roller and roller guide a reduction in the frictional wear on both components is achieved.
  • the surfaces of the roller guides contacting the cylinder inner surface are preferably cylindrical, as a result of which optimal guidance of the piston-roller arrangement in the cylinder is achieved. Since the roller normally does not experience any pressure loads in the axial direction, it would also be conceivable to design the surface of the roller guide, which rests on the inner surface of the cylinder, in a rotationally symmetrical or spherical segment-like manner with respect to the axis of rotation of the roller. In this case, a fixed connection between the roller guide and roller would be possible both in the stroke direction of the piston and in the direction of rotation of the roller. This would have the advantage that, during operation of the radial piston motor, there is no longer any friction between the roller and roller guides and the friction occurring between the roller guide and the inner surface of the cylinder is considerably reduced.
  • the piston on the end section facing away from the roller can have a flattening which is oriented perpendicularly with respect to the axis of rotation of the cylinder block and which is attached to a corresponding contact Surface of the anti-rotation device is present, whereby the rotational position of the piston in the cylinder and the roller relative to the stroke curve is clearly specified. It has also proven to be an effective measure if the cylinder has at least two cylinder sections of different inner diameters and the piston accordingly has at least two piston sections of different diameters adapted to the corresponding cylinder diameters. In this case, the anti-rotation device is provided in the cylinder section with the smaller inside diameter and the flattening is accordingly provided on the piston section with the smaller diameter.
  • the additional anti-rotation device provides better guidance of the piston in the cylinder compared to the conventional anti-rotation device mentioned at the outset, since according to the present invention there is a large-area sliding contact between the piston and the anti-rotation device.
  • the anti-rotation device preferably has a cross-section in the form of a segment of a circle, viewed in the stroke direction of the piston, with an arc corresponding to the inner surface of the cylinder and a chord corresponding to the flattening.
  • the manufacturing outlay in terms of fixing the anti-rotation device in the cylinder can be reduced in that the anti-rotation device is fixed in the cylinder by means of a pin which is connected to the cylinder Access hole is inserted in a blind hole aligned with the access hole in the cylinder block.
  • FIG. 1 shows a longitudinal section of a preferred embodiment of the radial piston engine according to the invention.
  • FIG. 2 shows a cross section through the cylinder block in FIG. 1 along the line INI;
  • FIG. 3a shows a section through the cylinder block in FIG. 2 along the line III-III shown on a larger scale
  • Fig. 4 shows a section through the cylinder block along the line IV-IV in
  • Fig. 5 is a perspective view of the roller guide
  • Fig. 6 shows a section through the cylinder block along the line VI-VI in
  • the radial piston motor 2 essentially consists of two housing parts 4 and 6 and a cam ring 8 arranged between the two housing parts 4 and 6.
  • the two housing parts 4 and 6 and the cam ring 8 are by means of screws 10 screwed together coaxially and fluid-tight.
  • a lifting curve 12 is formed with a plurality of cams 14, as can be seen in particular in FIG. 2.
  • a cylinder block 18 is arranged within the lifting ring 8 so as to be rotatable about a longitudinal or rotational axis 16. As can be seen in FIGS.
  • the cylinder block 18 has a central recess 20 provided with internal teeth.
  • the output shaft 24 is rotatably supported by a bearing 30 relative to the two housing parts 4 and 6 and the cam ring 8.
  • the bearing 30 comprises two tapered roller bearings 32 and 34, which are housed in the housing part 4 and can transmit high axial and radial forces.
  • the other end section 26 of the output shaft 24 protruding from the housing part 4 has a shaft flange 28 for attachment to a drive element (not shown) of a device to be driven, for example to a wheel of a loader.
  • a plurality of cylinders 36 which are directed radially outward with respect to the axis of rotation 16 and have a cylinder axis 37 perpendicular to the axis of rotation 16, are also formed in the cylinder block 18.
  • the cylinder 36 has a cylinder section 38 with a large inner diameter lying radially outside with respect to the axis of rotation 16 and a cylinder section 40 lying radially inside with a small inside diameter.
  • the cylinder section 38 is open on the substantially cylindrical outer peripheral surface 42 of the cylinder block 18.
  • there is an access bore 43 parallel to the longitudinal or rotational axis 16 and opening into the cylinder section 40, via which hydraulic fluid 2 is supplied or removed during operation of the radial piston motor.
  • a piston 44 is received in the cylinder 36 and, as shown in FIG. 3b, has piston sections 46 and 48.
  • the piston section 46 has a diameter which essentially corresponds to the inside diameter of the cylinder section 38.
  • the piston section 48 has on its outer circumference two flats 48a and 48b which, as can be seen in FIG. 6, are oriented perpendicular to the axis of rotation 16.
  • the diameter of the outer circumference of the piston section 48 corresponds to the inner diameter of the cylinder section 40.
  • the flattened portion 48b defines a bearing. surface that bears against a correspondingly provided contact surface 50b of an anti-rotation device 50 described in more detail below.
  • the flattened portion 48a faces the access bore 43.
  • the pistons 44 are selectively pressurized in such a way that they carry out a lifting movement in the direction of the lifting ring 8. They are each supported by a corresponding roller 54 on the lifting curve 12 formed on the lifting ring 8.
  • the axial width B of the cam ring in this embodiment of the radial piston motor 2 essentially corresponds to the axial length of the rollers 54.
  • a bearing 56 is formed on the end section of the respective piston sections 46 facing the cam ring 8, in which the respective roller 54 is accommodated rotatably about an axis of rotation 58 relative to the piston 44.
  • a roller guide 60 is arranged on each of the two end faces 54a and 54b of the roller 54, as a result of which the axial position of the roller 54 in the cylinder 36 and thus relative to the piston 44 and the stroke curve 12 is predetermined.
  • the roller guides 60 are each arranged in one of the spaces formed between the end faces 54a and 54b of the roller 54, the piston 44 and the cylinder inner surface of the cylinder 36.
  • FIG. 5 shows a perspective view of the roller guide 60 which, viewed in the piston stroke direction, has an essentially circular segment-shaped cross section.
  • each roller guide 60 On the chord side facing the end face 54a or 54b of the roller 54, each roller guide 60 has a cylindrical projection 62 which is axial with respect to the axis of rotation 58 and which has a corresponding central recess 54c or 54d on the end faces 54a or 54b of the roller 54 in Intervention stands.
  • the cylindrical arc side 63 of each roller guide 60 lies against the inner surface of the cylinder 36.
  • the length of the axial projection 62 is somewhat greater than the depth of the recess 54c or 54d, so that between the surface of the roller guide 60 around the central projection 62 and each ring surface on the end face 54a or 54b of the roller 54 around the central recess 54c or 54d there is a game.
  • the roller guides 60 are carried along by the respective roller 54 in the operation of the radial piston motor 2, that is to say when the piston moves in the piston stroke direction.
  • the width of the cam ring corresponds to the length of the rollers, there is no butt contact between the roller guides and the cam ring during operation of the radial piston motor according to this embodiment, regardless of whether the roller guides protrude beyond the roller in the piston stroke direction.
  • the wear of both components can be considerably reduced as a result of the relative speed between roller guides and roller that occurs during operation of the radial piston motor, since the friction between the two components occurs in an area in which the relative speed is relatively low.
  • a so-called anti-rotation device 50 is provided on the inner cylinder surface of the cylinder section 40 opposite the access bore 52, which has the function of rotating the piston 44 in the cylinder 38 about a cylinder axis 37 prevent.
  • the decisive factor here is that a certain rotational position of the piston 44 with respect to the cylinder axis 37 and thus the roller 54 with respect to the stroke curve 12 is maintained.
  • the anti-rotation device 50 is fastened to the cylinder block 18 by means of a pin 76, for example a taper pin, cylindrical pin or notch pin, in the manner shown in FIG. 3a or FIG. 6.
  • FIG. 7 shows a perspective view of the anti-rotation device 50, which, like the roller guide 60, viewed in the piston stroke direction, has a substantially circular segment-shaped cross section, the cylindrical arc side 50a on the cylinder inner surface of the cylinder section 40 and the chord side 50b on the piston section 48 of the piston 44 trained flat 48b is present.
  • a cylindrical recess 78 is formed in the anti-rotation device 50, in which sits the part of the pin 76 that emerges from the blind hole 84 in the cylinder block 18, which is aligned with the access bore 43 protrudes.
  • the reference numeral 66 represents a fluid control, by means of which hydraulic fluid is supplied to the respective cylinder spaces or discharged from the respective cylinder spaces via the access bores 43 during operation of the radial piston motor 2.
  • the fluid control 66 is arranged in the housing part 6 in a fluid-tight and rotationally fixed manner.
  • the fluid control 66 has two circumferential grooves 68 and 70 which are separate from one another and are each connected to a fluid channel 72 and 74, respectively.
  • the fluid channels 72 and 74 alternately connect to the axial inlet bores 43, which are formed in the cylinder block 18 and each communicate with one of the cylinder spaces.
  • the pistons 44 are controlled by means of hydraulic fluid via the fluid channels 68, 70, 72 and 74, the access bores 43 and the cylinder spaces in such a way that they are pressed radially outward with respect to the axis of rotation 16. They are supported via the respective roller 54 on the stroke curve 12 of the stroke ring 8, as a result of which the cylinder block 18 is finally caused to rotate about the axis of rotation 16. The direction of rotation is selected by the control method. Torque is transmitted to the output shaft 24 via the positive connection of the output shaft 24 to the cylinder block 18. This is supported by the tapered roller bearings 32 and 34 of the bearing 30.
  • a drive element for example a wheel of a loader, not shown here, which is connected to the output shaft 24 via the flange section 28, thus receives a torque.
  • FIGS. 8a and 8b show modifications of the roller guides described in connection with the above embodiment of the radial piston motor according to the invention.
  • the roller guide 90 shown in FIG. 8a differs from the roller guide 60 shown in FIG. 5 in that it is rounded on the upper outer surface facing the cam ring 8 in accordance with the outer circumference of the roller 54 and is designed in such a way that it is stroke direction does not protrude beyond the outer circumference of the roller. Since in this case the roller guide 90 does not protrude beyond the outer circumference of the roller 54 and is also connected to the roller 54 in a manner fixed against displacement in the piston stroke, the roller guide 90 - naturally only together with the roller 54 according to the invention - could also be used for a conventional radial piston motor with a cam ring, the cam ring of which has a width which is greater than the length the roll 54.
  • the roller guide 92 shown in FIG. 8b has a surface 93 that is rotationally symmetrical or spherical segment-like with respect to the axis of rotation 58 of the roller 54 on the side facing the inner cylinder surface . Since the roller and thus also the roller guides normally do not experience too high axial loads during operation of the radial piston motor, a spherical segment-like configuration of the roller guides should not lead to a reduction in the service life of the roller guides.
  • the roller guides 92 could be positively and / or non-positively connected to the roller 54 not only in the piston stroke direction but also in the direction of rotation of the roller 54, so that no more friction occurs between the roller and the roller guide.
  • the friction occurring between the roller guide 92 and the cylinder inner surface would also be considerably reduced.
  • the roller guides 90 and the roller 54 then no longer rotate relative to one another, the positive and / or non-positive connection between the roller guide and roller could also be realized in any other way. It would also be conceivable to form the roller and the roller guides in one piece, ie to provide the roller guides on the roller.
  • FIGS. 9a and 9b show further possibilities for connecting the roller guides to the roller.
  • the roller guide 98 in FIG. 9b is characterized by a conical projection 99, which is in engagement with a corresponding, conically shaped, central recess 101 on the roller 100.
  • the roller guide engages with the roller without play, but, as in the previous examples, the contact area between roller 100 and roller guides 98 is relocated to a central area with respect to the axis of rotation 58.
  • an anti-rotation device 50 is provided which prevents the piston 44 in the cylinder 36 and thus the roller 54 from rotating relative to the lifting curve 12.
  • the rollers are normally in constant contact with the stroke curve, which automatically determines the rotational position of the roller and thus of the piston, it is not absolutely necessary to provide an anti-rotation device.
  • Fig. 10a the cylinder and piston construction is simplified considerably, since no production-related measures have to be carried out either on the piston 102 or on the cylinder block.
  • an anti-rotation device 106 can be created for the piston 104 without the piston and cylinder having to be designed in a stepped manner.
  • the present invention thus creates a technically optimized radial piston motor with a cam ring and a cylinder block arranged rotatably about an axis of rotation with respect to the cam ring with a plurality of cylinders aligned in the radial direction of the cylinder block.
  • a piston which is displaceable in the radial direction and is supported in the cylinders by a roller, is supported on the cam ring.
  • the roller is mounted in a bearing provided on the piston so as to be rotatable about an axis of rotation parallel to the axis of rotation of the cylinder block and is axially supported with respect to its axis of rotation in the cylinder by means of roller guides arranged on its end faces.
  • the radial piston motor according to the invention is characterized in particular by the fact that the roller guides are connected to the respective roller so as to be non-displaceable in the piston stroke direction and are accordingly carried along by the respective roller during a load stroke as well as an empty stroke of the piston in the piston stroke direction, as a result of which no contact of the Roller guides with the cam ring takes place.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Hydraulic Motors (AREA)
  • Transmission Devices (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)

Abstract

La présente invention concerne un moteur à pistons radiaux optimisé du point de vue technique, qui comporte une bague à came et un bloc-cylindres disposé de façon à pouvoir tourner autour d'un axe de rotation par rapport à la bague à came et présente une pluralité de cylindres dirigés dans le sens radial du bloc-cylindres. Dans chaque cylindre se trouve un piston pouvant être déplacé dans le sens radial, qui repose sur la bague à came par l'intermédiaire d'un galet. Ce galet est monté sur le piston de façon à pouvoir tourner autour d'un axe de rotation parallèle à celui du bloc-cylindres et repose axialement, par rapport à son axe de rotation dans le cylindre, contre des guides de galet disposés sur ses faces. Le moteur à pistons radiaux selon l'invention se caractérise en particulier par le fait que les guides de galet sont solidaires en déplacement du galet qui leur est associé, dans le sens de la course du piston, et sont ainsi entraînés par le galet aussi bien lorsque le piston effectue une course en charge qu'une course à vide, aucun contact ne se produisant entre les guides de galet et la bague à came. Les pistons sont montés bloqués en rotation par un dispositif séparé du système de guidage à rouleaux.
EP99915563A 1998-03-10 1999-03-10 Moteur a pistons radiaux avec guidage des galets Expired - Lifetime EP1062426B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19810372A DE19810372A1 (de) 1998-03-10 1998-03-10 Radialkolbenmotor mit Rollenführung
DE19810372 1998-03-10
PCT/EP1999/001551 WO1999046504A2 (fr) 1998-03-10 1999-03-10 Moteur a pistons radiaux avec guidage des galets

Publications (2)

Publication Number Publication Date
EP1062426A2 true EP1062426A2 (fr) 2000-12-27
EP1062426B1 EP1062426B1 (fr) 2002-10-02

Family

ID=7860418

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99915563A Expired - Lifetime EP1062426B1 (fr) 1998-03-10 1999-03-10 Moteur a pistons radiaux avec guidage des galets

Country Status (5)

Country Link
US (1) US6494127B1 (fr)
EP (1) EP1062426B1 (fr)
JP (1) JP2002506172A (fr)
DE (2) DE19810372A1 (fr)
WO (1) WO1999046504A2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003046379A1 (fr) * 2001-11-21 2003-06-05 Robert Bosch Gmbh Piston-poussoir

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19810372A1 (de) 1998-03-10 1999-09-16 Mannesmann Rexroth Ag Radialkolbenmotor mit Rollenführung
WO2010046952A1 (fr) * 2008-10-24 2010-04-29 パスカルエンジニアリング株式会社 Dispositif générateur de pression hydraulique
US8276376B2 (en) * 2009-05-06 2012-10-02 Terra Drive Systems, Inc. Hydraulic circuit with selectively actuated motor
JP2014141957A (ja) * 2012-12-28 2014-08-07 Mitsubishi Heavy Ind Ltd ラジアルピストン式油圧機械および風力発電装置
US10267149B2 (en) 2013-08-05 2019-04-23 Lester J. Erlston Combined electric and hydraulic motor
FR3052820B1 (fr) * 2016-06-16 2019-07-19 Poclain Hydraulics Industrie Piston pour une machine hydraulique a pistons radiaux a frottements limites
CN111412195A (zh) * 2020-04-22 2020-07-14 宁波恒通诺达液压股份有限公司 具有抗冲击功能的液压马达及工程运输车辆
DE102021213182B4 (de) 2021-11-23 2025-03-20 Festo Se & Co. Kg Verfahren zur Ansteuerung eines pneumatischen Mehrzylindermotors und Antriebssystem mit einem pneumatischen Mehrzylindermotor

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3922956A (en) 1971-11-09 1975-12-02 Renold Ltd Hydraulic motors
SU513167A1 (ru) * 1973-11-20 1976-05-05 Ордена Трудового Красного Знамени Институт Горного Дела Имени А.А.Скочинского Объемный гидродвигатель
US3978771A (en) * 1975-04-21 1976-09-07 Clark Equipment Company Mechanical piston retention for free wheeling
GB2086991A (en) 1980-08-26 1982-05-19 Staffa Products Ltd Improvements in and relating to hydraulic motors
FR2582058B1 (fr) * 1985-05-15 1989-06-30 Poclain Hydraulics Sa Mecanisme hydraulique, moteur ou pompe, muni de rouleaux montes sur les pistons et de moyens de maintien en position desdits rouleaux
DE3530979A1 (de) * 1985-08-30 1987-03-12 Rexroth Mannesmann Gmbh Radialkolbenmaschine
FR2651836B1 (fr) * 1989-09-14 1994-06-10 Poclain Hydraulics Sa Mecanisme, moteur ou pompe, a pistons supportant des rouleaux d'appui desdits pistons sur une came.
SE503563C2 (sv) 1991-06-25 1996-07-08 Haegglunds Denison Drives Ab Anordning vid hydraulkolvmotor
DE4421535A1 (de) 1994-06-20 1995-12-21 Schaeffler Waelzlager Kg Rollenstößel mit einer Käfighalterung
FR2727471A1 (fr) * 1994-11-30 1996-05-31 Poclain Hydraulics Sa Mecanisme, moteur ou pompe, a pistons munis de rouleaux d'appui sur une came
DE19602770C2 (de) * 1996-01-26 1998-01-29 Sauer Sundstrand Gmbh & Co Kolbenrollen-Führung für Radialkolbenaggregat
DE19618793B4 (de) * 1996-05-10 2007-01-18 Bosch Rexroth Aktiengesellschaft Radialkolbenmaschine
DE19618792B4 (de) * 1996-05-10 2007-01-18 Bosch Rexroth Aktiengesellschaft Radialkolbenmaschine
DE19810372A1 (de) 1998-03-10 1999-09-16 Mannesmann Rexroth Ag Radialkolbenmotor mit Rollenführung
DE19851324C1 (de) * 1998-11-06 2000-03-16 Sauer Sundstrand Gmbh & Co Hydraulischer Radialkolbenmotor mit Führungselementen zur axialen Führung von dessen Zylinderrollen und Werkzeug zur Montage der Führungselemente

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9946504A2 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003046379A1 (fr) * 2001-11-21 2003-06-05 Robert Bosch Gmbh Piston-poussoir

Also Published As

Publication number Publication date
US6494127B1 (en) 2002-12-17
DE59902931D1 (de) 2002-11-07
WO1999046504A3 (fr) 1999-12-09
DE19810372A1 (de) 1999-09-16
JP2002506172A (ja) 2002-02-26
EP1062426B1 (fr) 2002-10-02
WO1999046504A2 (fr) 1999-09-16

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