EP0102915B1 - Moteur hydraulique à piston radial - Google Patents

Moteur hydraulique à piston radial Download PDF

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Publication number
EP0102915B1
EP0102915B1 EP83710058A EP83710058A EP0102915B1 EP 0102915 B1 EP0102915 B1 EP 0102915B1 EP 83710058 A EP83710058 A EP 83710058A EP 83710058 A EP83710058 A EP 83710058A EP 0102915 B1 EP0102915 B1 EP 0102915B1
Authority
EP
European Patent Office
Prior art keywords
piston
roller
radial
hydraulic motor
motor according
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
EP83710058A
Other languages
German (de)
English (en)
Other versions
EP0102915A3 (en
EP0102915A2 (fr
Inventor
Einar Samuelsson
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.)
Hagglund and Soner AB
Original Assignee
Hagglund and Soner AB
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 Hagglund and Soner AB filed Critical Hagglund and Soner AB
Publication of EP0102915A2 publication Critical patent/EP0102915A2/fr
Publication of EP0102915A3 publication Critical patent/EP0102915A3/de
Application granted granted Critical
Publication of EP0102915B1 publication Critical patent/EP0102915B1/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
    • F03C1/0403—Details, component parts specially adapted of such engines
    • F03C1/0428—Supporting and guiding means for the pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F03C1/047—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 outer ends of the cylinders

Definitions

  • the present invention relates to a hydraulic radial piston motor according to the preamble of claim 1.
  • a radial piston motor is known from GB-A 864767.
  • Engines of the aforementioned type include multiple rollers that run along an in-wall cam curve in a motor housing and are influenced in the radial direction by associated pistons that slide in cylinders that are present in a cylinder block arranged in the motor housing.
  • the pistons are completely relieved of tangential forces by having journals on the axial ends of the rollers with bearings that run in radially directed slots in guide units that are rigidly connected to each side of the cylinder block are arranged.
  • the housing can either be stationary and the cylinder block rotatable, or conversely the cylinder block stationary and the housing rotatable.
  • the motor is connected to a drive shaft.
  • the motor is connected to a wheel or a cable drum for a winch or the like.
  • the piston force is transmitted to the roller via a connecting rod-like piston rod.
  • the roller is supported in its center in a bearing, which is arranged at the outer end of the piston rod, and is provided with roller tracks on each side of the bearing.
  • the piston rod is supported in the piston at its inner end. The length of the roll increases with the width of the storage in the bar. The width of the runway in the motor housing is correspondingly wider, while its middle part remains unused.
  • a crosshead is attached to the radially outer end of the piston, and two bearing points are provided at each end of the crosshead, of which the inner one carries a roller against a cam curve and the outer one by means of a roller bearing is guided in a radial slot.
  • the attachment between the crosshead (roller holder) and the piston is made via spherical surfaces that allow the roller holder to move angularly relative to the piston.
  • a disadvantage of this known construction in addition to the relatively large axial extension, is the bending of the roller holder in its longitudinal direction.
  • the roll holder is arranged like a support clamped at both ends, on which the force of the piston acts in the middle. This causes a deflection, which leads to an alternating load on the rolls and roll holder, which results in premature wear.
  • a radial piston motor is known from FR-A 2033554, in which the rollers lie directly in cylindrical-shell-shaped depressions on the radially outer end faces of the pistons.
  • An additional roll holder is therefore not available here.
  • the bearing is lubricated through a bore through the piston, whereby a certain hydrostatic bearing of the roller takes place at the same time.
  • This embodiment has the disadvantage that the bearings formed directly on the cylinder must also absorb the tangential forces. For this reason, the piston must have a relatively large play in the cylinder and may only seal against the cylinder wall with a single cylinder ring. The design results in a relatively high lateral load on the bearing and the piston-cylinder guide.
  • the invention has for its object to develop a hydraulic radial piston motor of the type mentioned, in which the bearing, the piston-cylinder guide and the roller holder are exposed to relatively low mechanical stresses, in particular harmful stresses in or between the piston and the roller holder and between the roller holder and roller be avoided.
  • the radial piston motor should be very compact and have the smallest possible radial and axial dimensions.
  • the pistons sliding in the cylinders in the cylinder block can be provided at their outer ends with a spherical bearing surface which interacts with a corresponding bearing surface of a roller holder, without this resulting in bending moments in the roller holder.
  • This is achieved in that the rollers running along the cam curve are mounted directly in the roller holders with a cylindrical bearing seat surface, this bearing being designed as a hydrostatic bearing. Thanks to the spherical mounting of the roller holder on the front of the piston, the roller holder can be tilted in all directions around the center of the spherical bearing, so that stress on the piston due to tilting moments is avoided.
  • the pistons of the engine have a continuous axial bore, which expediently has a larger diameter in the outer part than in the inner part.
  • the reel seat that supports the reels has a guide pin that protrudes into the outer part of the larger diameter hole.
  • the roller holder and piston can be held together by a strong spring which is fastened in the guide pin mentioned and on the inner part of the piston.
  • the roles Holder can be designed so that it encompasses the roll by more than 180 °, whereby the roll is fixed in the holder.
  • the roll holder can also be designed with a smaller angle of coverage than 180 ° C., the roll holder or the motor being provided with other devices for fixing a roll in the roll holder or for guiding the roll.
  • the cylindrical bearing seat surface for the roller is provided with a delimited hydrostatic bearing surface, so that a suitable balance of the force acting on the roller is achieved.
  • the wing can be delimited by grooves that create a gap seal.
  • the radial pressure forces acting on the roll holder and the piston are hydrostatically balanced to more than 80%, preferably 85 to 90%.
  • Fig. 1 denotes a disc, the inner peripheral wall of which is formed as a cam curve 2.
  • This in-wall cam cam is arranged in a rotatable housing, not shown, which can drive a wheel or a winch.
  • a cylinder block 3 with a plurality of cylinders 4 is arranged in a stationary manner.
  • On each side of the cylinder block 3 there are disc-shaped guide members 5 with slots 6 for guiding the rollers 7 and for absorbing tangential forces which occur when the rollers 7 are pressed against the cam curve 2.
  • the guide members 5 are firmly connected to the cylinder block 3 and thus also stationary.
  • Pistons 8 slide in the cylinders. These are connected to the rollers 7 via connecting rods 10 similar to connecting rods.
  • rollers are rotatably supported in a bearing, not shown, on the outer end of the rods.
  • a circumferential slide 11 for distributing pressure medium to the cylinders 4 is arranged in the cylinder block 3.
  • the fully illustrated pressure lines and the cylinders just connected to them are filled with pressure medium of high pressure, while the others are not filled, or the pressure medium in them is not under pressure.
  • 20 denotes the motor housing of a hydraulic motor according to the invention, which is a non-rotating motor housing.
  • This has two end walls 21 and 22 and a cam disk 23 mounted between them with an in-wall cam curve 24 (FIG. 3).
  • the end walls 21 and 22 and the cam disk 23 are held together by bolts 27.
  • a cylinder block 25 with a shaft journal 26 is rotatably supported in the end walls 21 and 22 of the motor housing 20 by means of bearings 28, 30 and 31.
  • the part 32 of the cylinder block is connected to a shaft, not shown, with a conical coupling 33.
  • cylinder block 25 there are a plurality of radially directed cylinders 34, in which pistons 35 slide.
  • pistons have through bores 36, the radially outer part 36a of which has a larger diameter than the rest of the bore 36.
  • the pistons are provided with a spherical, spherical zone-shaped bearing seat surface 37 at their radially outer ends.
  • Drive rollers 38 run along the cam curve 24.
  • These drive rollers 38 are mounted in roller holders 40 which are designed like hydrostatic bearings.
  • roller holders 40 are provided with a spherical, spherical zone-shaped bearing seat surface 41 which is adapted to the bearing seat surface 37 of the pistons 35. The roller holder 40 can thus be tilted in all directions in relation to the piston 35.
  • the roller holders 40 have a guide pin 42 which projects into the bore 36a.
  • the pistons 35 and the roller holder 40 are held together by a spring 43 which is fastened with pins 44 and 45 in the guide pin 42 and in the piston 35, respectively.
  • the roller holder 40 encompasses the roller 38 by more than 180 °, as a result of which the roller 38 is radially fixed in the holder 40. Because of this enclosure, the holder 40 consists of two parts 40a and 40b, which are held together with bolts 46 (Fig. 4).
  • the rollers 38 are provided with flanges 47 for guiding them in the axial direction in relation to the cam disk 23. Furthermore, pins 48 are provided on the axial ends of the rollers, which support roller bearings, the outer ring of which forms a guide roller 50. The bearings are fixed on the pin 48 by means of washers 51 and locking rings 52. Two disk-shaped guide units 53 with radially directed slots 54 are firmly connected to the cylinder block 25 by bolts 55. The guide rollers 50 transmit tangential forces acting on the rollers 38 to the cylinder block 25 via the guide units 53.
  • Pressure medium is passed via a flat slide valve with two slide rings 56 and 57 to and from the cylinders 34 of the cylinder block 25.
  • the ring 56 is connected to the cylinder block in such a way that it rotates with it.
  • the ring 57 is connected to the end wall 22 in such a way that it does not rotate, but axially in relation nis to the ring 56 is displaceable.
  • the ring 56 has through holes 58 which open in the middle of channels 60 in the cylinder block 25, which channels 60 lead to the cylinders.
  • the ring 57 has through holes 61 which serve in the middle of channels 62 in the end wall 22 for the supply or discharge of pressure medium.
  • the inward end of the channel 62 is drilled out further in diameter, and a sleeve 64 is arranged in the bore 63 thus created, which is pressed against the slide ring 57 by a spring 65 and the pressure medium acting on the inner end face of the sleeve.
  • Through holes 66 are present in the slide ring 57 with an opening 67 of smaller diameter on the side facing the ring 56.
  • Pistons 68 are arranged in these boreholes 66, which bear against the end wall 22.
  • the forces between the pistons 35 and the roller holders 40 and the forces between the rollers 38 and the roller holders 40 are largely hydrostatically balanced.
  • the bearing pressures on the abutting bearing surfaces 37 and 41 of the piston 35 or roller holder 40 and between the bearing surfaces 69 of the roller holder and the surface of the roller 38 are small.
  • the pressure medium in the cylinder 34 has free access through the bore 36 through the piston 35 to the space 78 between the piston 35 and the holder 40.
  • a channel 70 is provided in the roller holder 40, through which the pressure medium in the space 78 has access to the recess 71 has in the bearing surface 69 of the roll holder 40. As best shown in FIGS.
  • this recess is surrounded by at least one, preferably two, annular grooves 72 and 73.
  • the groove 72 communicates with the recess 71 via a flat channel 74.
  • the groove 73 and the groove 75 connected to it and leading to the side edge of the roller holder are drainage grooves which discharge pressure medium which penetrates between the roller 38 and the annular sealing surface 76 formed by the roller holder 40 between the grooves 72 and 73.
  • the size and the width of the sealing surface 76 delimited by the grooves 72 and 73 are chosen so large that the desired hydrostatic balancing of the forces acting on the roller 38 and a low surface pressure on the sealing surface 76 are obtained.
  • the loss of lubricating pressure medium that passes through the sealing surface 76 is small. Furthermore, the drainage groove 73 prevents the pressure medium from reaching the outer sections of the roll holder and deforming it in a disturbing manner.
  • a well-defined sealing surface is obtained which is only insignificantly influenced by deformation of the central area of the roller holder due to the piston force.
  • the diameter of the spherical, spherical-zone-shaped bearing surface 37 at the end of the piston 35 and the bearing surface 41 of the roller holder 40 interacting with this bearing surface 37 are also dimensioned with a view to the desired hydrostatic balancing.
  • the structure of the slide ring 56 is best seen in FIGS. 6 and 7.
  • the hole 61 changes its shape on the side that slides on the slide ring 57 and here has an elongated, oval shape.
  • part of the pin (42) is provided with a diameter such that a throttle gap is formed between this part of the pin and the bore in the piston (35) surrounding it. This ensures that the pressure medium loss is kept very small when a lift occurs.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
  • Reciprocating Pumps (AREA)

Claims (12)

1. Moteur hydraulique à piston radiaux avec un carter (20) qui comporte un disque à came (23) à came intérieure (24), avec un bloc-cylindres (25) posédant plusieurs cylindres (34) dirigés radialement, avec des pistons (35) coulissant dans ces cylindres (34), avec des supports de rouleaux (40) possédant une surface d'appui cylindrique, avec des rouleaux (38) roulant sur la came (24), avec des unités de guidage (53) qui sont solidarisées avec le bloc-cylindres (25) du moteur et qui possèdent des fentes de commande (54) dirigées axialement, et avec des bouts d'arbre (48) sur les rouleaux (38) qui portent des paliers de guidage (50) roulant dans les unités de guidage (53) et qui transmettent les forces tangentielles qui agissent sur les rouleaux (38), aux unités de guidage (53) et par voie de conséquence, sur le bloc-cylindres (25), le support des rouleaux (40) et les pistons (35) étant des éléments de construction séparés, qui sont reliés entre eux de telle façon que sont possibles dans toutes les directions, des déplacements angulaires entre les supports de rouleaux (40) et les pistons (35), caractérisé par le fait que les rouleaux (38) portent, avec leur partie centrale, dans le sens longitudinal, contre la came (24) et que les rouleaux (38) sont montés hydrostatiquement dans les supports des rouleaux associés (40).
2. Moteur hydraulique à pistons radiaux selon la revendication 1, caractérisé par le fait que les pistons (35) et les supports de rouleaux (40) sont pourvus de surfaces d'appui (37, 41) en forme de zones sphériques, destinées à leur appui mutuel.
3. Moteur hydraulique à pistons radiaux selon l'une des revendications 1 ou 2, caractérisé par le fait que les pistons (35) du moteur comportent un perçage axial traversant (36), et que les supports de rouleaux (40) comportent un tourillon de guidage (42) qui pénètre dans le perçage (36) ménagé dans les pistons (35).
4. Moteur hydraulique à pistons radiaux selon l'une des revendications précédentes, caractérisé par le fait que les paliers hydrostatiques sont reliés par l'intermédiaire d'un canal (70) ménagé dans des supports de rouleaux (40), avec le perçage (36) ménagé dans le piston, et que par l'intermédiaire de cette liaison, un lubrifiant est susceptible d'être amené.
5. Moteur hydraulique à pistons radiaux selon l'une des revendications précédentes, caractérisé par le fait que les forces qui agissent du support de rouleaux (40) sur les pistons (38), sont au moins en grande partie compensés par voie hydrostatique.
6. Moteur hydraulique à pistons radiaux selon l'une des revendications précédentes, caractérisé par le fait que les supports de rouleaux (40) sont pourvus d'au moins une gorge annulaire (72, 73) et que la partie de la surface d'appui (69) du support de rouleaux, concernée par cette gorge, est pourvue d'une cavité (71).
7. Moteur hydraulique selon l'une des revendications 1 à 5, caractérisé par le fait que les supports de boulons (40) sont pourvus d'une première gorge annulaire intérieure (72) et d'une seconde gorge annulaire extérieure de drainage (73), que la surface annulaire qui est délimitée par les deux gorges annulaires (72, 73) constitue une surface d'étanchéité (76), et que la zone de la surface d'appui (69) du support de rouleaux entourée par la première gorge (72), est pourvue d'une cavité (71).
8. Moteur hydraulique selon l'une des revendications 1 à 5, caractérisé par le fait que les supports de rouleaux (40) sont pourvus, dans leur partie centrale, d'une cavité (71) et d'une gorge de drainage (73) qui entoure cette cavité, et que la surface des supports de rouleaux , qui est délimitée par la cavité (71) et par la gorge de drainage (73), constitue une surface d'étanchéité annulaire qui sert à l'appui des rouleaux (38).
9. Moteur hydraulique selon l'une des revendications précédentes, caractérisé par le fait que les pistons (35), d'une part, et les supports de rouleaux (40), d'autre part, sont maintenus assemblés par un ressort (43) disposé dans les pistons (35).
10. Moteur hydraulique selon l'une des revendications précédentes, caractérisé par le fait que les supports de rouleaux (40) entourent avec le palier hydrostatique (69), sur plus de 180°, la surface du rouleau (38) qui se déplace le long de la came (24).
11. Moteur hydraulique selon l'une des revendications précédentes, caractérisé par le fait que les forces qui agissent sur un rouleau (38) sont compensées hydrostatiquement au moins pour 80% dans le palier-porteur (69).
12. Moteur hydraulique selon l'une des revendications 3 à 11, caractérisé par le fait qu'une partie du tourillon de guidage (42) possède un diamètre tel qu'entre cette partie du tourillon de guidage et le perçage (36a) du piston (35) qui l'entoure, forme une fente d'étranglement qui empêche une perte importante du milieu sous pression, au décollement du piston (35) du support de rouleaux (40).
EP83710058A 1982-09-08 1983-08-31 Moteur hydraulique à piston radial Expired EP0102915B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE8205097A SE456517B (sv) 1982-09-08 1982-09-08 Hydraulisk radialkolvmotor
SE8205097 1982-09-08

Publications (3)

Publication Number Publication Date
EP0102915A2 EP0102915A2 (fr) 1984-03-14
EP0102915A3 EP0102915A3 (en) 1985-03-06
EP0102915B1 true EP0102915B1 (fr) 1987-05-13

Family

ID=20347753

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83710058A Expired EP0102915B1 (fr) 1982-09-08 1983-08-31 Moteur hydraulique à piston radial

Country Status (5)

Country Link
US (1) US4522110A (fr)
EP (1) EP0102915B1 (fr)
JP (1) JPS5965578A (fr)
DE (1) DE3371550D1 (fr)
SE (1) SE456517B (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013160149A2 (fr) 2012-04-28 2013-10-31 Robert Bosch Gmbh Machine a piston radiaux
DE102013217714A1 (de) 2013-09-05 2015-03-05 Robert Bosch Gmbh Hydrostatische Radialkolbenmaschine
DE102016214978A1 (de) 2016-08-11 2018-02-15 Robert Bosch Gmbh Hydrostatische Radialkolbenmaschine
DE102016214976A1 (de) 2016-08-11 2018-02-15 Robert Bosch Gmbh Hydrostatische Radialkolbenmaschine und Verfahren zum Betreiben einer hydrostatischen Radialkolbenmaschine
DE102016214967A1 (de) 2016-08-11 2018-02-15 Robert Bosch Gmbh Hydrostatische Radialkolbenmaschine
EP3511568A1 (fr) 2018-01-10 2019-07-17 Robert Bosch GmbH Agencement d'étanchéité d'arbre et machine à pistons radiaux

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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013160149A2 (fr) 2012-04-28 2013-10-31 Robert Bosch Gmbh Machine a piston radiaux
DE102012008623A1 (de) 2012-04-28 2013-10-31 Robert Bosch Gmbh Radialkolbenmaschine
WO2013160149A3 (fr) * 2012-04-28 2014-05-01 Robert Bosch Gmbh Machine a piston radiaux
DE102013217714A1 (de) 2013-09-05 2015-03-05 Robert Bosch Gmbh Hydrostatische Radialkolbenmaschine
DE102016214978A1 (de) 2016-08-11 2018-02-15 Robert Bosch Gmbh Hydrostatische Radialkolbenmaschine
DE102016214976A1 (de) 2016-08-11 2018-02-15 Robert Bosch Gmbh Hydrostatische Radialkolbenmaschine und Verfahren zum Betreiben einer hydrostatischen Radialkolbenmaschine
DE102016214967A1 (de) 2016-08-11 2018-02-15 Robert Bosch Gmbh Hydrostatische Radialkolbenmaschine
EP3511568A1 (fr) 2018-01-10 2019-07-17 Robert Bosch GmbH Agencement d'étanchéité d'arbre et machine à pistons radiaux

Also Published As

Publication number Publication date
SE8205097L (sv) 1984-03-09
JPS5965578A (ja) 1984-04-13
US4522110A (en) 1985-06-11
EP0102915A3 (en) 1985-03-06
JPH0549820B2 (fr) 1993-07-27
DE3371550D1 (de) 1987-06-19
EP0102915A2 (fr) 1984-03-14
SE456517B (sv) 1988-10-10
SE8205097D0 (sv) 1982-09-08

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