EP1099055A1 - Moteur a pistons radiaux avec elements de guidage de galets - Google Patents

Moteur a pistons radiaux avec elements de guidage de galets

Info

Publication number
EP1099055A1
EP1099055A1 EP99934645A EP99934645A EP1099055A1 EP 1099055 A1 EP1099055 A1 EP 1099055A1 EP 99934645 A EP99934645 A EP 99934645A EP 99934645 A EP99934645 A EP 99934645A EP 1099055 A1 EP1099055 A1 EP 1099055A1
Authority
EP
European Patent Office
Prior art keywords
roller
cylinder
axis
machine according
radial piston
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
EP99934645A
Other languages
German (de)
English (en)
Other versions
EP1099055B1 (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 EP1099055A1 publication Critical patent/EP1099055A1/fr
Application granted granted Critical
Publication of EP1099055B1 publication Critical patent/EP1099055B1/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

Definitions

  • the invention is based on a radial piston machine, the pistons of which are pressurized on the inside and are each supported on a roller on the cam ring which is axially held by roller guides on the end faces and which has the other features from the preamble of patent claim 1.
  • wedge piece with a circular segment-like cross-section viewed in the stroke direction of the piston, 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. 0
  • 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 5 cylinder wall, without being permanently connected to any of these components. Due to this freely movable arrangement of the wedge piece relative to the roller in the piston direction, the piston takes the wedge pieces in the direction of the cam ring during a load stroke. There is still no contact between the wedge pieces and the cams formed on the cam ring. In the subsequent On the other hand, idle stroke of the piston pushes the wedge pieces against the cams formed on the cam ring and is pushed inwards.
  • each of the two wedge pieces on the side facing the roller has a driver-like projection which extends in a recess provided on the piston between the piston and roller in the direction of the other wedge piece.
  • the wedge pieces are taken from the roller back into the cylinder when the piston is idle.
  • one of the two wedge pieces on the side facing the cylinder wall has an elongated groove into which a bolt held on the cylinder wall in the form of a screw, clamp or the like engages and in this way prevents rotation of the piston in the cylinder and thus of the roller relative to the cam ring.
  • An additional part is therefore required to prevent the wedge piece and thus the piston and roller from rotating with respect to the axis of the cylinder, so that the production outlay is high.
  • the aim of the invention is to develop a radial piston machine with the features from the preamble of claim 1 so that it can be manufactured with less effort while ensuring reliable operation.
  • a roller guide has a projection on its side facing away from the roller, while the cylinder is provided with a groove running in the axial direction, which groove projects the projection of the roller guide in
  • the roller guides generally consist of a plastic material, so that the protrusion on the roller guide can be easily worked out of the solid material or, if the roller guide is produced by injection molding, can be molded on at the same time.
  • a groove in the cylinder can be milled out after the cylinder has been worked out. If it advantageously extends inwards from the open end of the cylinder, it can also be obtained by first making a small hole in the cylinder block, which is cut when a cylinder is being worked out.
  • the groove in the cylinder extends inwards to radially outside a point at which the underside of the piston facing away from the roller is in its extended dead center.
  • the position of the inner end of the groove, the position of a piston seal held on the piston and sealing the gap between it and the cylinder and the stroke of the piston are matched to one another in such a way that the piston seal does not reach the area of the groove.
  • the projection on the roller guide is a bar running in the axial direction of the cylinder, so that a certain length is available for the positive connection between the projection on the roller guide and the groove of the cylinder.
  • the bar on a roller guide is preferably located in the center of the roller guide, so that the roller guide is indifferent to the direction in which rotation of the piston and the roller is prevented and forces at the strongest point of the roller guide be introduced into this.
  • the roller guide can be inserted into the space between the roller and the cylinder in two positions rotated by 180 ° relative to each other if the projection or the strip is symmetrical to a plane running perpendicular to the axis of the cylinder at half the height of the roller guide .
  • the contour of a groove of the cylinder is preferably formed by a circular arc, because then, as already indicated, the groove can be worked out particularly easily.
  • both roller guides of a roller are secured against rotation to the cylinder block, the forces required for securing are divided between two roller guides, so that the projection or the strip on the roller guides can be relatively low and the grooves in the cylinder can be relatively flat.
  • FIG. 2 shows a section along the line II-II from FIG. 1 with pistons and roller guides in view
  • FIG. 3 shows a section along the line III-III from FIG. 2
  • FIG. 4 shows a partial longitudinal section through a second exemplary embodiment with a different shape of the roller guides and
  • FIG. 5 shows a section "taken along the line VV of Fig. 4
  • I O mainly used as a radial piston engine and has a housing 12 which is composed essentially of two housing pots 13 and 14 and a cam ring 15 arranged between them. The three parts mentioned are held together by screws 10 coaxially and in a fluid-tight manner.
  • the inner surface of the cam ring 15 is protruding as a cam 16 with a plurality of
  • cams 17 formed, as can be clearly seen from Figure 2.
  • the cam ring 15 there is a cylinder block 18 which is rotatable about an axis of rotation 19 coinciding with the axes of the housing parts.
  • the cylinder block 18 has an inner toothing, a central passage 20, in which an end section 21 of an output shaft 22, which is provided with an outer toothing corresponding to the inner toothing of the passage 20, is axially displaceably received.
  • the output shaft 22 is rotatably supported relative to the housing 12 via a bearing arrangement 30.
  • the bearing arrangement comprises two tapered roller bearings 31 and 32, which are housed in the housing part 13 and can transmit high axial and radial forces.
  • the second end section 33 of the output shaft 22 protrudes from the housing part 13 and, outside of this, has a shaft flange 34 for attachment to a drive element (not shown) of a device to be driven, for example on a wheel of a loader.
  • a multiplicity of cylinders 35 which are radially aligned in a star shape with respect to the axis of rotation 19 and are open towards the cam ring 15, are formed in the cylinder block 18 and are regarded as circular cylinders with the same diameter throughout, each having a cylinder axis 36 perpendicular to the axis of rotation 19 of the cylinder block 18 can.
  • each cylinder 35 has a central flat recess 37 with a reduced diameter, so that an annular shoulder 38 is created as a contact surface for the piston 45 located in the cylinder.
  • Each cylinder 35 is assigned an access bore 41 running in the cylinder block 18 parallel to its axis of rotation 19, starting from one end of the cylinder block and opening into the cylinder on both sides of the shoulder 38, via which hydraulic fluid is supplied and discharged during operation of the radial piston motor.
  • Each cylinder 35 also has in its wall two grooves 39 diametrically opposite each other in the direction of the axis of rotation 19 of the cylinder block, the contour of which, as can be seen in particular from FIG.
  • the working spaces of the cylinders 35 are alternated in pairs depending on the relative position between the cylinder block 18 and the housing part 12 and offset with respect to one another via the respective access bore 39 connected to the high pressure side of a pressure medium source or relieved of pressure.
  • a force acts on a piston 45 toward the outside in the direction of the cam ring 15.
  • the piston is supported on the cam ring 15 by a roller 48.
  • This is located in a receptacle of the piston 45, in which it is encompassed by more than 180 °, so that it can only be mounted in the direction of its axis 49.
  • a thin bearing shell 50 made of a bearing metal, on which the roller rests, is clipped into each receptacle.
  • the rollers 48 are tons with two end faces 51, 52 lying perpendicular to the axis 49 and, when the pistons 45 are displaced radially inward in the cylinders 35 when they hit a cam 16 of the cam 17, up to over half into the cylinders 35 on. This means that their length must be less than the diameter of a cylinder 35 and that in a wide stroke range of the pistons 45 there is a distance between the circular edges formed by the end faces and the cylindrical surface of a roller and the wall of the cylinders 35. Without additional measures, the rollers could move in the direction of their axis 49 and hit the cylinder block 18 during the return stroke of the piston. This could damage the parts and cause the engine to fail.
  • a roller guide 53 is arranged in front of each of the two end faces 51 and 52 of a roller 48 and the position of each roller 48 in the direction of its own axis with respect to a cylinder 35 and thus with respect to a piston 45 and with respect to the stroke curve 16 is thereby predetermined.
  • the two roller guides 53 for each roller 48 are each arranged in a space present between the end face 51 or 52 of the roller 48, the piston 45 and the cylinder wall of the cylinder 35 and are identical to one another.
  • a roller guide 53 In the piston stroke direction, ie viewed in the direction of the axis 36 of a cylinder 35, a roller guide 53 has an essentially circular segment cross section.
  • the roller guides rest against the end faces 51 and 52 of a roller 48 with a closed, flat surface.
  • the roller guides facing the roller 48, they have a circular cylindrical pin 54 which is axial with respect to the axis 49 of a roller and which engages suckingly in a corresponding central recess 55 on the end face 51 and 52, respectively.
  • the length of the pin 54 is somewhat greater than the depth of a recess 55, so that there is a small distance between the ring surface of a roller guide 53 around the pin 54 and the corresponding ring surface on the end face 51 or 52 'of a roller 48.
  • roller guides 53 are removed from the roller 48 during retraction and extension of the pin 54 Pistons 45 taken away.
  • the diameter of the roller guides 53 according to the exemplary embodiment according to FIGS. 1 to 3 is equal to the diameter of a roller 48.
  • roller guides are moved outwards by the piston 45 and inwards by the cams of the cam ring 15.
  • the substantially cylindrical outer surface 56 of each roller guide 53 facing away from a roller 48 lies against the wall of the cylinder 35.
  • the roller guides 53 cannot be rotated with respect to the axis of rotation 49 of a roller 48.
  • the relative rotary movement between the roller and roller guides takes place on the end faces 51 and 52 of the roller.
  • the roller guides extend a roller 48, so to speak, and adapt it to the circular cylindrical cross section of a cylinder 35, so that the rollers cannot move in the direction of their axis in the entire stroke of a piston 45.
  • each roller guide 53 is provided in the center of its outer surface 56 with a bar 57 running in the direction of the axis 36 over the entire height of a roller guide, the cross section of which is adapted to the cross section of the grooves 39 of the cylinder 35 and is positively received in the direction of rotation about the axis 36 of the cylinder 35.
  • the bar 57 can be easily formed on the roller guides 53 made of a plastic material.
  • the reference numeral 66 denotes a commutator, via which hydraulic fluid is supplied to the working spaces of the cylinders 35 via the access bores 41 or discharged from the working spaces during operation of the radial piston motor.
  • the commutator is arranged in the housing part 14 in a fluid-tight and rotationally fixed manner. Between it and the housing part 14, two separate annular spaces 68 and 70 are formed, which are connected to an inlet channel 71 and outlet channel 72 leading to the outside. From the end face of the commutator 66 facing the cylinder block 18, a number of axial blind bores 73, which cut the annular space 68 and which correspond to the number of cams 17 of the lifting curve 16, extend uniformly.
  • each two blind bores 73 also run from the front face of the commutator and at the same distance from the axis of rotation 19 as the blind bores 73 are shorter blind bores 74 which are connected to the annular space 70.
  • hydraulic fluid is displaced without pressure via the bore 41 of the cylinder block 18 and via one of the blind bores 74.
  • the bore 41 is not covered. Kung with the corresponding bore 74 and shortly thereafter in overlap with one of the bores 73.
  • hydraulic fluid is supplied to the working space, so that the piston 45 is pushed outwards and a torque 17 is generated by a cam 17 when the roller 48 runs off.

Landscapes

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

Abstract

L'invention concerne un moteur hydraulique à pistons radiaux présentant un anneau de levage (15) et un bloc-cylindres (18) placé de manière à pouvoir tourner autour d'un axe de rotation par rapport à l'anneau de levage, ledit bloc-cylindres comportant une pluralité de cylindres (15) orientés dans le sens radial du bloc-cylindres. Dans chaque cylindre est placé un piston coulissant (45) qui prend appui sur l'anneau de levage par l'intermédiaire d'un galet (48). Ce dernier (48) est monté sur le piston, de manière à pouvoir tourner autour d'un axe de rotation parallèle à l'axe de rotation du bloc-cylindres, et maintenu axialement dans le cylindre, en direction de son axe de rotation, par l'intermédiaire d'éléments de guidage de galets qui se trouvent devant ses faces frontales et sont bloqués en rotation par rapport à l'axe du cylindre, vis-à-vis du bloc-cylindres. L'invention vise à bloquer en rotation autour de l'axe du cylindre, le piston et le galet, de façon simple. A cet effet, au moins un des éléments de guidage d'un galet est directement bloqué en rotation par rapport au bloc-cylindres, sans élément supplémentaire.
EP99934645A 1998-07-21 1999-07-09 Moteur a pistons radiaux avec elements de guidage de galets Expired - Lifetime EP1099055B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19832696A DE19832696A1 (de) 1998-07-21 1998-07-21 Radialkolbenmaschine mit Rollenführungen
DE19832696 1998-07-21
PCT/EP1999/004835 WO2000005502A1 (fr) 1998-07-21 1999-07-09 Moteur a pistons radiaux avec elements de guidage de galets

Publications (2)

Publication Number Publication Date
EP1099055A1 true EP1099055A1 (fr) 2001-05-16
EP1099055B1 EP1099055B1 (fr) 2003-06-25

Family

ID=7874761

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99934645A Expired - Lifetime EP1099055B1 (fr) 1998-07-21 1999-07-09 Moteur a pistons radiaux avec elements de guidage de galets

Country Status (5)

Country Link
US (1) US6443047B1 (fr)
EP (1) EP1099055B1 (fr)
JP (1) JP2002521606A (fr)
DE (2) DE19832696A1 (fr)
WO (1) WO2000005502A1 (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE517873C2 (sv) * 1997-04-10 2002-07-30 Haegglunds Drives Ab Kolv till en hydraulisk radialkolvmotor samt hydraulisk radialmotor med sådan kolv
DE102008006123A1 (de) 2008-01-25 2009-07-30 Robert Bosch Gmbh Radialkolbenmaschine
DE102011083571A1 (de) * 2011-09-28 2013-03-28 Robert Bosch Gmbh Stößelbaugruppe für eine Kraftstoffhochdruckpumpe sowie Kraftstoffhochdruckpumpe
JP5734506B2 (ja) * 2012-06-29 2015-06-17 三菱重工業株式会社 流体作動装置及び風力発電装置
DE102012212579B4 (de) * 2012-07-18 2018-11-22 Continental Automotive Gmbh Rollenstößelanordnung für eine Radialkolbenpumpe mit zwei Sicherungselementen für die Laufrolle des Rollenstößels
FR3024503B1 (fr) * 2014-07-31 2019-06-21 Poclain Hydraulics Industrie Dispositif de carter de distribution pour une machine hydraulique
FR3026791B1 (fr) * 2014-10-03 2019-04-19 Poclain Hydraulics Industrie Mecanisme hydraulique muni de moyens de guidage en translation des pistons
FR3030645B1 (fr) * 2014-12-17 2019-10-11 Poclain Hydraulics Industrie Appareil hydraulique a pistons radiaux
FI130485B (en) * 2021-08-12 2023-09-29 Black Bruin Oy RADIAL PISTON HYDRAULIC MOTOR WITH A HOLLOW ROTATING SHAFT WITHIN THE MOTOR

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2086991A (en) * 1980-08-26 1982-05-19 Staffa Products Ltd Improvements in and relating to hydraulic motors
SE456517B (sv) * 1982-09-08 1988-10-10 Hegglund & Soner Ab Hydraulisk radialkolvmotor
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
FR2588616B1 (fr) * 1985-10-16 1988-01-08 Poclain Hydraulics Sa Mecanisme, moteur a pompe, a au moins deux cylindrees actives distinctes.
DE3828131A1 (de) * 1988-08-18 1990-02-22 Rexroth Mannesmann Gmbh Radialkolbenmaschine
DE3926354A1 (de) * 1989-08-09 1991-02-14 Rexroth Mannesmann Gmbh Spuelventil
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.
DE4004932C2 (de) * 1990-02-16 1995-04-13 Rexroth Mannesmann Gmbh Radialkolbenmaschine
DK292690D0 (da) * 1990-12-10 1990-12-10 Htc As Motor- eller pumpeaggregat
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

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO0005502A1 *

Also Published As

Publication number Publication date
DE59906111D1 (de) 2003-07-31
US6443047B1 (en) 2002-09-03
JP2002521606A (ja) 2002-07-16
EP1099055B1 (fr) 2003-06-25
DE19832696A1 (de) 2000-01-27
WO2000005502A1 (fr) 2000-02-03

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