EP0102915A2 - Moteur hydraulique à piston radial - Google Patents

Moteur hydraulique à piston radial Download PDF

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Publication number
EP0102915A2
EP0102915A2 EP83710058A EP83710058A EP0102915A2 EP 0102915 A2 EP0102915 A2 EP 0102915A2 EP 83710058 A EP83710058 A EP 83710058A EP 83710058 A EP83710058 A EP 83710058A EP 0102915 A2 EP0102915 A2 EP 0102915A2
Authority
EP
European Patent Office
Prior art keywords
roller
piston
motor according
hydraulic motor
roller holder
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
EP83710058A
Other languages
German (de)
English (en)
Other versions
EP0102915B1 (fr
EP0102915A3 (en
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
Haegglund and Soener AB
Original Assignee
Hagglund and Soner AB
Haegglund and Soener 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, Haegglund and Soener 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 invention relates to a hydraulic radial piston motor according to the preamble of claim 1.
  • the motor contains a plurality of rollers which run along an in-wall cam curve in a motor housing and are influenced in the radial direction by associated pistons which slide in cylinders which are arranged in a in the motor housing Cylinder block are present.
  • 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 this are arranged.
  • the housing can 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 via a connecting rod-like Transfer the piston rod to the roller.
  • 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.
  • the invention has for its object to develop a hydraulic radial piston motor of the type mentioned, which is very compact on the one hand and has small radial and axial dimensions, and on the other hand, the width of the entire cam curve is used as an effective runway. Furthermore, it should be achieved that the force is transmitted to the roller via the pressure medium in such a way that the pressure medium acts directly on the roller, so that the stresses on the bearing carrying the roller are reduced and consequently the transmission of larger forces is possible and / or the service life of the wearing parts is increased. Finally, roller holder and piston should be designed so that imperfections in the shape and operational deformations of the engine components do not cause any harmful stresses in or between the piston and roller holder and between the roller holder and roller.
  • the pistons sliding in the cylinders in the cylinder block are provided with a spherical bearing surface at their outer end.
  • the rollers running along the cam curve are mounted in roller holders with a cylindrical bearing seat surface which is designed as a hydrostatic bearing and is provided with a spherical bearing surface which bears against the spherical bearing surface of the piston.
  • the roll holder can be tilted in all directions around the center of the spherical bearing. The fact that the roller holder can tilt relative to the piston in this way prevents stress on the piston due to tilting moments that are based on roller holder movements caused by imperfections in the cam curve and the guides of the rollers.
  • the pistons of the engine have a continuous axial bore. tion, which advantageously has a larger diameter in the outer part than in the inner part.
  • the reel seat that carries 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 roll 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 inclination 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 by Grooves that delimit a gap seal must be delimited.
  • 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 designed 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 rod-like rods 10 connected.
  • the central part of the rollers is rotatably mounted in a bearing (not shown) at 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 shown with a cone 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 roll holder 40 can thus in all Rich lines are tilted in relation to the piston 35. As a result, neither tilting moments nor lateral forces act on the pistons.
  • 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, there are pins 48 on the axial ends of the rollers, which support roller bearings, the outer ring thereof. 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 conducted 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 is axially displaceable in relation to the ring 56.
  • 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 are in the middle of channels 62 in the end wall 22 for supply or discharge serve from 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 provided in the slide ring 57 with an opening 67 of smaller diameter on the side facing the ring 55.
  • 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 roll holder and the surface of the roll 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 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.
  • a part of the pin (42) is provided according to the invention 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 lifting takes place.

Landscapes

  • 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)
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
SE8205097 1982-09-08
SE8205097A SE456517B (sv) 1982-09-08 1982-09-08 Hydraulisk radialkolvmotor

Publications (3)

Publication Number Publication Date
EP0102915A2 true EP0102915A2 (fr) 1984-03-14
EP0102915A3 EP0102915A3 (en) 1985-03-06
EP0102915B1 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 (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0524437A1 (fr) * 1991-06-25 1993-01-27 Hägglunds Denison Drives Ab Moteur hydraulique à piston
DE19816452B4 (de) * 1997-04-10 2010-06-10 Hägglunds Drives AB Kolben für einen Hydraulikmotor
WO2012159725A1 (fr) * 2011-05-23 2012-11-29 Robert Bosch Gmbh Machine hydrostatique à pistons radiaux et piston pour une machine hydrostatique à pistons radiaux
FR3010741A1 (fr) * 2013-09-18 2015-03-20 Poclain Hydraulics Ind Cartouche formant un moteur ou une pompe hydraulique preassemble a pistons radiaux

Families Citing this family (27)

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Publication number Priority date Publication date Assignee Title
FI73789C (fi) * 1983-12-07 1987-11-09 Partek Ab Hydraulisk motor.
DE3531632A1 (de) * 1985-09-05 1987-03-12 Rexroth Mannesmann Gmbh Radialkolbenmaschine
WO1988000639A1 (fr) * 1986-07-23 1988-01-28 Sea Shelf Engineering Pty Ltd. Moteur hydrocyclique
IT1221428B (it) * 1988-05-18 1990-07-06 Corghi Elettromecc Spa Gruppo di comando pluricilindrico,azionato a fluido,particolarmente adatto per macchine smontagomme
AUPN840796A0 (en) * 1996-03-01 1996-03-28 Raffaele, Peter Fluid machines
CN2284883Y (zh) * 1996-07-12 1998-06-24 陈智 纯滚活齿传动
US5996324A (en) * 1998-01-22 1999-12-07 Case Corporation Hydraulic feeder reverser
DE19832696A1 (de) * 1998-07-21 2000-01-27 Mannesmann Rexroth Ag Radialkolbenmaschine mit Rollenführungen
FR2834011B1 (fr) * 2001-12-24 2004-03-19 Poclain Hydraulics Ind Moteur hydraulique a pistons radiaux
FR2834012B1 (fr) * 2001-12-24 2004-03-19 Poclain Hydraulics Ind Moteur hydraulique a pistons radiaux
ITMO20020287A1 (it) * 2002-10-02 2004-04-03 I Societa Apparecchiature Idra Uliche Spa Sa Macchina idraulica con cilindri radiali ad alto rendimento.
EP1557562B1 (fr) * 2004-01-23 2009-06-17 Manfreda, Marija Système distributeur pour un moteur hydraulique à piston radial
CN100387832C (zh) * 2005-09-07 2008-05-14 周沛凝 一种低速大扭矩液压驱动机构
DE102006058076A1 (de) * 2006-12-07 2008-06-19 Zf Friedrichshafen Ag Hydraulischer Radialkolbenmotor
CA2710270C (fr) * 2007-12-21 2014-06-17 Carleton Life Support Systems, Inc. Compresseur radial a came et ensembles compresseurs a cames
FR2955903B1 (fr) * 2010-02-01 2012-03-16 Poclain Hydraulics Ind Sous-ensemble formant hydrobase pour moteurs hydrauliques et procede d'assemblage
DE102012008623A1 (de) 2012-04-28 2013-10-31 Robert Bosch Gmbh Radialkolbenmaschine
DE102013217714A1 (de) 2013-09-05 2015-03-05 Robert Bosch Gmbh Hydrostatische Radialkolbenmaschine
GB201512473D0 (en) * 2015-07-16 2015-08-19 Blagdon Actuation Res Ltd Radial piston pumps and motors
US11002268B2 (en) 2015-07-27 2021-05-11 Cobham Mission Systems Davenport Lss Inc. Sealed cavity compressor to reduce contaminant induction
US10408201B2 (en) * 2015-09-01 2019-09-10 PSC Engineering, LLC Positive displacement pump
DE102016214967A1 (de) 2016-08-11 2018-02-15 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
US10400817B2 (en) 2016-11-22 2019-09-03 Woodward, Inc. Radial bearing device
EP3511568B1 (fr) 2018-01-10 2022-03-23 Robert Bosch GmbH Agencement d'étanchéité d'arbre et machine à pistons radiaux
FR3128692B1 (fr) * 2021-10-29 2026-01-30 Safran Landing Systems Dispositif d’entraînement en rotation d’une roue comprenant un moteur hydraulique à pistons radiaux et des moyens de verrouillage des pistons en position rentrée.

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FR1347220A (fr) * 1962-11-16 1963-12-27 Dispositif hydraulique de transformation d'énergie à vitesse varlable
GB1125561A (en) * 1964-09-02 1968-08-28 British Aircraft Corp Ltd Improvements in hydraulic motors and pumps
GB1180513A (en) * 1968-05-23 1970-02-04 Cam Rotors Ltd Radial Piston Fluid Pressure Motor
FR2033554A5 (fr) * 1969-02-27 1970-12-04 Pr Motors Ltd
US3789741A (en) * 1971-07-26 1974-02-05 Fmc Corp Hydrostatic bearing for radial piston pump
GB1463495A (fr) * 1973-04-09 1977-02-02
US4144799A (en) * 1976-06-25 1979-03-20 Ponchaux Jean Luc Fluid machine
CS212800B2 (en) * 1976-07-15 1982-03-26 Ivan J Cyphelly Delivery apparatus with hydrostatic torque transfer by cylindrical pistons
GB2044348B (en) * 1979-03-01 1983-01-06 Poclain Hydralics Fluid mechanism with axially movable valve-seat
GB2086991A (en) * 1980-08-26 1982-05-19 Staffa Products Ltd Improvements in and relating to hydraulic motors

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0524437A1 (fr) * 1991-06-25 1993-01-27 Hägglunds Denison Drives Ab Moteur hydraulique à piston
DE19816452B4 (de) * 1997-04-10 2010-06-10 Hägglunds Drives AB Kolben für einen Hydraulikmotor
WO2012159725A1 (fr) * 2011-05-23 2012-11-29 Robert Bosch Gmbh Machine hydrostatique à pistons radiaux et piston pour une machine hydrostatique à pistons radiaux
FR3010741A1 (fr) * 2013-09-18 2015-03-20 Poclain Hydraulics Ind Cartouche formant un moteur ou une pompe hydraulique preassemble a pistons radiaux

Also Published As

Publication number Publication date
SE456517B (sv) 1988-10-10
SE8205097D0 (sv) 1982-09-08
JPH0549820B2 (fr) 1993-07-27
US4522110A (en) 1985-06-11
EP0102915B1 (fr) 1987-05-13
EP0102915A3 (en) 1985-03-06
SE8205097L (sv) 1984-03-09
DE3371550D1 (de) 1987-06-19
JPS5965578A (ja) 1984-04-13

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