EP1062426B1 - Moteur a pistons radiaux avec guidage des galets - Google Patents

Moteur a pistons radiaux avec guidage des galets Download PDF

Info

Publication number
EP1062426B1
EP1062426B1 EP99915563A EP99915563A EP1062426B1 EP 1062426 B1 EP1062426 B1 EP 1062426B1 EP 99915563 A EP99915563 A EP 99915563A EP 99915563 A EP99915563 A EP 99915563A EP 1062426 B1 EP1062426 B1 EP 1062426B1
Authority
EP
European Patent Office
Prior art keywords
roller
cylinder
piston
radial piston
piston engine
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
EP99915563A
Other languages
German (de)
English (en)
Other versions
EP1062426A2 (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

Images

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 the axial guidance of the rollers over which the pistons are located Support the cam ring.
  • each wedge piece has the one facing the roll A flat surface lying on the front side of the roll and on the side facing away from the roller, the inner surface of the cylinder contacting cylindrical surface.
  • This wedge is also in the Space taken up between the roller, piston and inner surface of the cylinder without to be firmly connected to any of these components.
  • each of the two wedge pieces on the Roll facing side on a driver-like projection which is in a recess provided on the piston between piston and roller in Extends towards the other wedge piece. Because the wedge pieces in this case taken from the roller back into the cylinder when the piston is idle can therefore not be a shock contact come between the wedge pieces and the cams. as a result of high relative speed between the roller and the driver-like Projections of the wedge pieces that contact the outer circumference of the roller, However, there can be high abrasion on the driver-like projections come. With increasing wear of the driver-like projections the wedge pieces could move in the piston stroke direction finally enlarge such that there is a butt contact between the Wedge pieces and the cam could come up. Another disadvantage of this Type is that on the roller guides driver-like projections and Piston recesses need to be formed, which increases manufacturing costs and thus increases the manufacturing costs.
  • one of the two has to ensure cylinders Wedge pieces on the side facing the inner surface of the cylinder an elongated Slip into a screw, clamp that goes through the cylinder wall or the like engages and in this way a rotation of the Prevents piston in the cylinder and thus the roller against the cam ring.
  • DE-A1-4421535 discloses a roller tappet for a radial piston pump.
  • the roller plunger includes a roller shoe in which a roller is positively guided, via which the roller tappet on a cam ring
  • There is a holding element in to fix the role on the roller shoe Form of a cage holder encompassing the role.
  • the holding element is composed, for example, of two end plates, each are held on the roller shoe by means of unwinding and on the side connecting elements running on the roller, which fix the roller.
  • the holding element via two end plates and thus connected bends held on the roller shoe, the role on the face side with two guide pins arranged centrally to the longitudinal axis of the roller is provided, which protrude into recesses in the face plates.
  • DE-A1-4421535 is no indication that the Roll each axially on the end elements arranged on the end support the inner wall of the cylinder.
  • Disadvantages of the object of the present invention are therefore to create a technically optimized radial piston motor that stands out a low manufacturing outlay and at the same time a reliable function Operation distinguished.
  • roller guides in the piston stroke direction i.e. both during of the load stroke as well as during the empty stroke, taken from the respective role the roller guides can be sized in this way that they do not protrude beyond the outer circumference of the role, so that no between the roller guides and the cam ring Butt contact takes place This ultimately leads to an increase in the service life of the roller guides and thus for reliable operation of the radial piston motor as a whole Roller guides material saved.
  • the width of the cam ring can also be reduced to a width that corresponds at most to the width of the rolls. In this way it is disregarded of the total weight of the radial piston motor also the manufacturing technology Effort and thus the manufacturing costs with regard to precision machining the stroke curve of the stroke ring is significantly reduced.
  • connection of the roller and roller guides that is fixed in the stroke direction can be implemented through simple manufacturing measures.
  • the roller guides on the front of the Roll facing side have a cylindrical projection which in a central, cylindrical recess formed on the end face of the roller can be used.
  • the Roller guides on the side facing the end of the roller Have recess in which a formed on the end face of the roller Lead can be used.
  • the recess and the one with the recess in However, the protruding engagement could also be conical. If the diameters of the recesses and the projections are dimensioned that they are small compared to the outside diameter of the roll, i.e.
  • the projections and the recesses are centered on one Focus the area around the axis of rotation of the reel, and face the protrusions engaging with the respective recesses in such a way that between the ring surface of the roller around the recess and the surface around the The lead of the roller guide is a game, decrease in the Operation of the radial piston motor on the outer periphery of the projection and peripheral speeds present on the inner peripheral wall of the recess and thus the relative speed between Role and roller guides. Because they are also spaced apart on the two Surfaces of the roller and roller guide no friction occurs, one will Reduction of frictional abrasion achieved on both components.
  • the surfaces of the roller guides contacting the inner surface of the cylinder are preferably cylindrical for the sake of simplicity, which ensures optimal guidance of the piston-roller arrangement in the cylinder is achieved. Since the roller normally does not have any compressive loads in the axial direction experienced, it would also be conceivable that on the inner surface of the cylinder adjacent surface of the roller guide with respect to the axis of rotation of the To form a role rotationally symmetrical or spherical segment. In this The case would even be one in the stroke direction of the piston as well as in the direction of rotation the role fixed connection between roller guide and role possible. This would have the advantage that in the operation of the radial piston motor between Roller and roller guides no longer occurs and the between The friction of the roller guide and the inner surface of the cylinder is considerable is reduced.
  • the piston can on the side facing away from the roller End section one perpendicular to the axis of rotation of the cylinder block have aligned flattening on a corresponding contact surface the anti-rotation is applied, whereby the rotational position of the piston in Cylinder and the roller against the stroke curve is clearly specified.
  • An effective measure has also been found when the cylinder at least two cylinder sections of different inner diameters and the piston accordingly at least two piston sections of different, diameter adapted to the corresponding cylinder diameters having.
  • the anti-rotation device is in the cylinder section the smaller inner diameter and the flattening accordingly on Piston section provided with the smaller diameter.
  • the measure will be a large area of pressure on the piston preserved and on the other hand only little to form the flattening Material removed from the piston.
  • the additional anti-twist device creates compared to the conventional anti-rotation device mentioned at the beginning better guidance of the piston in the cylinder, since according to the present Invention a large-area sliding contact between the piston and anti-rotation takes place.
  • the anti-rotation device preferably has one in the stroke direction of the piston viewed, circular segment-shaped cross section with one of the cylinder inner surface corresponding arc and one corresponding to the flattening Tendon.
  • the cylinder block usually has axial access holes anyway has, via which the hydraulic fluid reaches the respective cylinder spaces, can the production engineering effort in terms of fixing the Reduce the anti-twist device in the cylinder by using the anti-twist device is fixed in the cylinder by means of a pin that goes over the access hole inserted into a blind hole in the cylinder block aligned with the access hole becomes.
  • the radial piston motor 2 consists essentially, as shown in Fig. 1 from two housing parts 4 and 6 and one between the two Housing parts 4 and 6 arranged cam ring 8.
  • the two housing parts 4 and 6 and the cam ring 8 are coaxial and fluid-tight by means of screws 10 screwed together.
  • On the inner surface of the lifting ring 8 is a lifting curve 12 formed with a plurality of cams 14, as is special can be seen in Fig. 2.
  • the cam ring 8 Within the cam ring 8 is a around a longitudinal or rotational axis 16 arranged rotatably arranged cylinder block 18.
  • the cylinder block 18 has an internal toothing central recess 20 on.
  • a End section 22 of an output shaft 24 In this recess 20 is a End section 22 of an output shaft 24, with one of the internal teeth the recess 20 corresponding external teeth is provided axially slidably added.
  • the output shaft 24 is via a bearing 30 rotatable relative to the two housing parts 4 and 6 and the cam ring 8 stored.
  • the bearing 30 comprises two tapered roller bearings 32 and 34 which in the Housing part 4 are housed and transmit high axial and radial forces can.
  • the other end section 26 protruding from the housing part 4 the output shaft 24 has a shaft flange 28 for attachment to a Not shown drive element of a device to be driven, for example on a wheel of a loader.
  • the cylinder block 18 there are also a plurality of with respect to the Rotation axis 16 star-shaped radially outwardly directed cylinder 36 with a cylindrical axis 37 perpendicular to the axis of rotation 16.
  • the cylinder has 36 a cylinder section lying radially outside with respect to the axis of rotation 16 38 with a large inside diameter and a radially inside lying cylinder section 40 with a small inner diameter on.
  • the cylinder section 38 stands on the substantially cylindrical outer peripheral surface 42 of the cylinder block 18 open.
  • a piston 44 is received in the cylinder 36 which, as shown in FIG. 3b is shown has piston sections 46 and 48.
  • Piston section 46 has a diameter that is essentially the inner diameter of the Cylinder section 38 corresponds.
  • the piston section 48 has on its The outer circumference has two flats 48a and 48b, which, as shown in FIG see is aligned perpendicular to the axis of rotation 16.
  • the diameter the outer circumference of the piston section 48 corresponds to the inner diameter of the cylinder section 40.
  • the flattened portion 48b defines a contact surface, the one on a correspondingly provided contact surface 50b Anti-rotation lock 50 described in more detail below is present.
  • the flattened portion 48a faces the access bore 43.
  • the pistons 44 selectively pressurized in such a way that it has a lifting movement run towards the cam ring 8. They support each other a corresponding roller 54 on the lifting curve formed on the lifting ring 8 12 from.
  • the axial width B corresponds to the Hubrings in this embodiment of the radial piston motor 2 essentially the axial length of the rollers 54.
  • a bearing 56 is formed in the end section of the respective piston sections 46, in which the respective roller 54 relative to the piston 44 by one Rotation axis 58 is rotatably supported.
  • FIG. 5 shows a perspective view of the Roller guide 60, viewed in the piston stroke direction, essentially one has circular segment-shaped cross section.
  • each roller guide 60 has a cylindrical projection 62 that is axial with respect to the axis of rotation 58 on that with a corresponding central recess 54c or 54d the end faces 54a and 54b of the roller 54 is engaged.
  • the cylindrical Bow side 63 of each roller guide 60 lies on the inner surface of the cylinder Cylinder 36.
  • the length of the axial projection 62 is slightly larger 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 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 in the operation of the Radial piston motor 2, i.e. with a stroke movement of the pistons, in the piston stroke direction taken away from the respective roll 54.
  • the width of the cam ring corresponds to the length of the rollers in operation of the radial piston engine according to this embodiment, independently whether the roller guides in the piston stroke direction over the roller protrude, no butt contact between the roller guides and the Lifting ring instead.
  • the wear of both components due to the im Operation of the radial piston motor occurring relative speed between Reduce roller guides and roller considerably, since the friction between the two components occur in an area in which the relative speed is relatively low.
  • the anti-rotation device 50 is a cylinder pin by means of a pin 76, for example a taper pin or grooved pin attached to the cylinder block 18 in the manner as it is shown in Fig. 3a or Fig. 6. Fig.
  • FIG. 7 shows a perspective view of the Anti-rotation device 50, like the roller guide 60, in the piston stroke direction considered, 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 formed flattened portion 48b.
  • roller guide 60 which in this embodiment of the radial piston motor has a projection 62
  • in the anti-rotation device 50 is a cylindrical Recess 78 formed in which the part of the pin 76 is seated, which is made of the blind hole 84 in the cylinder block 18 aligned with the access hole 43 protrudes.
  • a fluid control is represented by reference numeral 66 by means of the hydraulic fluid in operation of the radial piston motor 2 via the access holes 43 fed to the respective cylinder rooms or from the respective Cylinder rooms is discharged.
  • the fluid control 66 is in the housing part 6 arranged fluid-tight and non-rotatable.
  • the fluid control 66 has two of them separate circumferential grooves 68 and 70, each with a Fluid channel 72 or 74 are connected.
  • the fluid channels 72 and 74 alternate with the axial access bores 43 in connection, which are formed in the cylinder block 18 and each communicate with one of the cylinder rooms.
  • Figures 8a and 8b show modifications of the context with the above embodiment of the radial piston engine according to the invention described roller guides.
  • the roller guide 90 shown in Fig. 8a differs from that 5 roller guide 60 shown in that it on the lifting ring 8th facing upper outer surface corresponding to the outer circumference of the roller 54 is rounded and designed in such a way that it is in the piston stroke direction does not protrude beyond the outer circumference of the roll. Because the roller guide 90 does not protrude beyond the outer circumference of the roller 54 in this case and also in the piston stroke direction in a manner fixed against displacement with the roller 54 stands, the roller guide 90 - of course, only together with the Roller 54 according to the invention also for a conventional radial piston motor be used with a cam ring, the cam ring one Has a width which is greater than the length of the roller 54.
  • roller guide 92 While the surfaces 63 contacting the cylinder inner surface the roller guides 60 previously cylindrical for simplicity the roller guide 92 shown in FIG. 8b has on the inner surface of the cylinder facing side with respect to the axis of rotation 58 of the roller 54 rotationally symmetrical or spherical segment-like surface 93. Since the Roller and thus also the roller guides in the operation of the radial piston motor should not normally experience excessive axial loads a spherical segment-like design of the roller guides does not become one Reduce the lifespan of the roller guides.
  • roller guides could 92 not only in the piston stroke direction but also in the direction of rotation of the Roller 54 are positively and / or non-positively connected to roller 54, so that there is no more friction between roller and roller guide.
  • essentially only linear arrangement of the roller guide 92 on the inner surface of the cylinder would also be that between the roller guide 92 and the inner surface of the cylinder considerably reduced. Since the roller guides 90 and the roller 54 are then no longer relative to each other could rotate, the positive and / or non-positive connection between roller guide and roller in any other way and Way to be realized. It would also be conceivable the role and the role guides to be formed in one piece, i.e. to provide the roller guides on the roller.
  • Figures 9a and 9b show further possibilities, the roller guides to relate to the role.
  • roller guide 94 according to FIG. 9a a recess 95 and the roller 96 a corresponding projection 97 on.
  • Friction occurs in an area where small relative speeds prevail between roller and roller guides.
  • the present one Invention not only limited to this; of course it would also be possible that the roller guides in the conventional sense, i.e. without play, immediately to be in contact with the role.
  • the roller guide 98 in Fig. 9b is characterized by a conical Projection 99 from that with a corresponding, conically shaped, centric Recess 101 is engaged on the roller 100.
  • the roller guide engages with the roller without play, however, as in the previous examples, the contact area between Roller 100 and roller guides 98 in one with respect to the axis of rotation 58 central area is relocated.
  • an anti-rotation device is 50 provided that a rotation of the piston 44 in the cylinder 36 and thus the roller 54 against the stroke curve 12 prevented.
  • an anti-rotation device since the roles normally in constant contact with the stroke curve, causing the Rotational position of the roller and thus the piston is determined automatically, it is it is not absolutely necessary to provide an anti-rotation device. This case is shown in Figure 10a.
  • the cylinder and piston construction is simplified essential, since neither on the piston 102 nor on the cylinder block production-related Measures must be taken.
  • the present invention thus creates a technically optimized Radial piston motor with a cam ring and one opposite the cam ring Cylinder block with a multiplicity arranged rotatably about an axis of rotation of cylinders aligned in the radial direction of the cylinder block.
  • Each cylinder has a piston that can be moved in the radial direction, which is supported by a roller on the cam ring.
  • the role is in one Piston provided storage about a to the axis of rotation of the cylinder block parallel axis of rotation rotatably supported and supported on its front sides arranged roller guides with respect to their axis of rotation in the cylinder axially.
  • the radial piston engine according to the invention is particularly notable characterized in that the roller guides in the piston stroke direction with the each role are connected to move and accordingly with both a load stroke and an empty stroke of the piston in the piston stroke direction be taken away from the respective role, so no Contact of the roller guides with the cam ring takes place.

Claims (11)

  1. Moteur à pistons radiaux (2) avec une bague de course (8) et avec un bloc-cylindres (18) disposé de manière tournante autour d'un axe de rotation (16) en face de la bague de course (8) et comportant une pluralité de cylindres radiaux (36) orientés en direction radiale du bloc-cylindres (18), dans lesquels se trouve respectivement un piston coulissant (44), qui s'appuie par l'intermédiaire d'un galet (54, 96, 100) sur la bague de course, le galet étant disposé sur le piston de manière à pouvoir tourner autour d'un axe de rotation (58) parallèle à l'axe de rotation (16) du bloc-cylindres (18) et s'appuyant dans le sens axial par rapport à l'axe de rotation (58) sur la paroi intérieure du cylindre (36) par l'intermédiaire de guides de galets (60, 90, 92, 94, 98) disposés sur les côtés frontaux, caractérisé en ce qu'en direction de la course du piston les guides de galets (60, 90, 92, 94, 98) sont reliés en solidarité de déplacement avec le galet respectif (54, 96, 100).
  2. Moteur à pistons radiaux selon la revendication 1, caractérisé en ce que sur le côté dirigé vers le côté frontal du galet (54, 100) les guides de galets (60, 90, 92, 98) comprennent une saillie (62, 99), qui peut être introduite dans un évidement (54c, 54d, 101) pratiqué dans le côté frontal du galet.
  3. Moteur à pistons radiaux selon la revendication 1, caractérisé en ce que sur le côté dirigé vers le côté frontal du galet (96) les guides de galets (96) comprennent un évidement (95), dans lequel peut être introduite une saillie (97) formée sur le côté frontal du galet.
  4. Moteur à pistons radiaux selon l'une des revendications 1 à 3, caractérisé en ce que sur le côté opposé au côté frontal du galet les guides de galets (60, 90, 94, 98) présentent une surface cylindrique, qui correspond à la surface intérieure des cylindres.
  5. Moteur à pistons radiaux selon l'une des revendications 1 à 3, caractérisé en ce que sur le côté opposé au côté frontal du galet les guides de galets (92) présentent une surface, qui est en symétrie de rotation ou en forme de segment de sphère par rapport à l'axe de rotation (58) du galet.
  6. Moteur à pistons radiaux selon la revendication 5, caractérisé en ce qu'en direction de rotation du galet les guides de galets (92) sont reliés en solidarité de rotation avec le galet.
  7. Moteur à pistons radiaux (2) selon l'une des revendications précédentes, caractérisé en ce que pour éviter une rotation du piston dans le cylindre, il existe une protection anti-rotation (50) disposée séparément par rapport aux guides de galets.
  8. Moteur à pistons radiaux selon la revendication 7, caractérisé en ce que sur sa section terminale opposée au galet le piston est muni d'un plat, qui s'appuie sur une surface d'appui correspondante de la protection anti-rotation.
  9. Moteur à pistons radiaux selon la revendication 8, caractérisé en ce que le cylindre comprend au moins deux sections de cylindre (38, 40) de différents diamètres et le piston par conséquent au moins deux sections de piston (46, 48) de différents diamètres, qui sont adaptées aux diamètres correspondants du cylindre, la protection anti-rotation étant prévue dans la section de cylindre (40) avec le plus petit diamètre et le plat dans la section de piston (48) avec le plus petit diamètre.
  10. Moteur à pistons radiaux selon la revendication 9, caractérisé en ce que la protection anti-rotation comprend, dans une vue en direction de la course du piston, une section en forme de segment de cercle avec un coude correspondant à la surface intérieure du cylindre et une corde correspondant au plat.
  11. Moteur à pistons radiaux selon l'une des revendications 7 à 10, caractérisé en ce que la protection anti-rotation est fixée sur la surface intérieure du cylindre de la section de cylindre (40) avec le plus petit diamètre à l'aide d'une broche (76) introduite par une forure d'accès (43) pour l'entrée et la sortie de fluide hydraulique dans le volume intérieur du cylindre, la broche (76) étant fixée dans un évidement (84) pratiqué dans le bloc-cylindres (18) et qui est en alignement avec la forure d'accès (43).
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 EP1062426A2 (fr) 2000-12-27
EP1062426B1 true 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 (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3258100A1 (fr) * 2016-06-16 2017-12-20 Poclain Hydraulics Industrie Piston pour une machine hydraulique à pistons radiaux à frottements limités
DE102021213182A1 (de) 2021-11-23 2023-05-25 Festo Se & Co. Kg Verfahren zur Ansteuerung eines pneumatischen Mehrzylindermotors und Antriebssystem mit einem pneumatischen Mehrzylindermotor

Families Citing this family (6)

* 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
DE10157076A1 (de) * 2001-11-21 2003-05-28 Bosch Gmbh Robert Stößelkolben
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

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

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3258100A1 (fr) * 2016-06-16 2017-12-20 Poclain Hydraulics Industrie Piston pour une machine hydraulique à pistons radiaux à frottements limités
FR3052820A1 (fr) * 2016-06-16 2017-12-22 Poclain Hydraulics Ind Piston pour une machine hydraulique a pistons radiaux a frottements limites
DE102021213182A1 (de) 2021-11-23 2023-05-25 Festo Se & Co. Kg Verfahren zur Ansteuerung eines pneumatischen Mehrzylindermotors und Antriebssystem mit einem pneumatischen Mehrzylindermotor

Also Published As

Publication number Publication date
WO1999046504A3 (fr) 1999-12-09
DE59902931D1 (de) 2002-11-07
DE19810372A1 (de) 1999-09-16
EP1062426A2 (fr) 2000-12-27
JP2002506172A (ja) 2002-02-26
US6494127B1 (en) 2002-12-17
WO1999046504A2 (fr) 1999-09-16

Similar Documents

Publication Publication Date Title
EP0102915B1 (fr) Moteur hydraulique à piston radial
DE3610569C2 (de) Scheibenbremse für Fahrzeuge
EP1886035B1 (fr) Palier pivotant a disques obliques
EP0162238B1 (fr) Machine à pistons axiaux, en particulier pompe du type à plateau incliné
EP2179175A1 (fr) Machine à piston axial du type à plateau oscillant, présentant un dispositif de réglage
EP2145107A1 (fr) Segment de retenue
EP1062426B1 (fr) Moteur a pistons radiaux avec guidage des galets
DE3909910C2 (fr)
EP1099055B1 (fr) Moteur a pistons radiaux avec elements de guidage de galets
DE102008046821A1 (de) Kurbelwelle für eine Brennkraftmaschine mit varibaler Verdichtung und Brennkraftmaschine mit variabler Verdichtung
EP1948373B1 (fr) Tete de cylindre de laminage d'un outil de laminage
DE19625551A1 (de) Spielfrei einstellbare Geradführung
WO2001011202A1 (fr) Dispositif de variation des temps de commande de soupapes d'un moteur a combustion, en particulier dispositif de reglage de l'arbre a cames avec roue a ailettes pivotantes
DE3811970A1 (de) Waelzlageranordnung
DE4232191C1 (de) Vorrichtung zum Verstellen der Exzentrizität eines exzentrischen Radiallagers
DE102019217204A1 (de) Axialkolbenmaschine mit in der Verteilplatte gelagerten Antriebswelle
WO2009050150A1 (fr) Galet de came destiné à être fixé dans un trou borgne ou dans un trou débouchant
DE2220164C3 (de) Reiheneinspritzpumpe für Brennkraftmaschinen
DE19643389C1 (de) Axialkolbenmaschine mit variabler Fixierung der Steuerscheibe
DE19602770C2 (de) Kolbenrollen-Führung für Radialkolbenaggregat
DE102013211819B4 (de) Bausatz mit einem Nockenwellenadapterstück für ein Nockenwellenende
DE102019216495B4 (de) Lageranordnung für die Lagerung eines Bohrkopfes in einer Tunnelbohrmaschine und Tunnelbohrmaschine
DE2623014A1 (de) Schneckengetriebe
DE495218C (de) ??stellvorrichtung fuer Lagerungen mit mehreren Kugellagern
EP0064563B1 (fr) Disposition de patin glissant pour machine à pistons radiaux

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20000906

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): DE FR GB IT

17Q First examination report despatched

Effective date: 20010913

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REF Corresponds to:

Ref document number: 59902931

Country of ref document: DE

Date of ref document: 20021107

RAP2 Party data changed (patent owner data changed or rights of a patent transferred)

Owner name: BOSCH REXROTH AG

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20030115

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20030703

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20070529

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20080318

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20080314

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20080329

Year of fee payment: 10

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20081001

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20090310

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20091130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090310

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20091123

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090310