[go: up one dir, main page]

EP0102915A2 - Radial-piston hydraulic engine - Google Patents

Radial-piston hydraulic engine Download PDF

Info

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)
French (fr)
Other versions
EP0102915B1 (en
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/en
Publication of EP0102915A3 publication Critical patent/EP0102915A3/en
Application granted granted Critical
Publication of EP0102915B1 publication Critical patent/EP0102915B1/en
Expired legal-status Critical Current

Links

Images

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)

Abstract

Hydraulischer Radialkolbenmotor mit einer Nockenscheibe (23), die eine inwandige Nockenkurve (24) hat, und einem Zylinderblock (25) mit mehreren Zylindern (34). In diesen Zylindern (34) gleiten Kolben (35), welche die Rollen (38) gegen die Nockenkurve (24) drücken, wodurch ein Drehmoment erzeugt wird. Die Rollen (38) sind mit Führungsrollen (50) versehen, die in Schlitzen (54) von Führungseinheiten (53) laufen, die Tangentialkräfte aufnehmen. Die Rollen (38) sind in Rollenhaltern (40) gelagert, die mit hydrostatischen Lagern ausgeführt sind, deren Lagerfläche (69) der Rollbahn der Rollen (38) angepaßt ist. Die Kolben (35) sind an ihrem radial äußeren Ende mit einer sphärischen kugelzonenförmigen Lagerfläche (37) versehen, die gegen eine entsprechende sphärische Lagerfläche (41) an den Rollenhaltern (40) anliegen. Diese Lagerung gestattet Winkelbewegung zwischen den Rollenhaltern und dem Kolben in allen Richtungen.Hydraulic radial piston motor with a cam disc (23), which has an in-wall cam curve (24), and a cylinder block (25) with a plurality of cylinders (34). Pistons (35) slide in these cylinders (34) and press the rollers (38) against the cam curve (24), whereby a torque is generated. The rollers (38) are provided with guide rollers (50) which run in slots (54) of guide units (53) which absorb tangential forces. The rollers (38) are mounted in roller holders (40) which are designed with hydrostatic bearings, the bearing surface (69) of which is adapted to the runway of the rollers (38). The pistons (35) are provided at their radially outer end with a spherical spherical zone-shaped bearing surface (37) which bear against the corresponding spherical bearing surface (41) on the roller holders (40). This bearing allows angular movement between the roller holders and the piston in all directions.

Description

Die Erfindung betrifft einen hydraulischen Radialkolbenmotor gemäß dem Oberbegriff des Anspruches 1. Der Motor enthält mehrere Rollen, die an einer inwandigen Nockenkurve in einem Motorgehäuse entlanglaufen und in radialer Richtung von zugeordneten Kolben beeinflußt werden, die in Zylindern gleiten, die in einem in dem Motorgehäuse angeordneten Zylinderblock vorhanden sind. Bei einer Ausführung eines Motors für schweren Betrieb sind die Kolben dadurch vollständig von tangentialen Kräften entlastet, daß an den axialen Enden der Rollen Zapfen mit Lagern vorhanden sind, die in radial gerichteten Schlitzen in Führungseinheiten laufen, die auf jeder Seite des Zylinderblocks in fester Verbindung mit diesem angeordnet sind. Es kann entweder das Gehäuse stationär und der Zylinderblock drehbar ausgebildet sein oder umgekehrt der Zylinderblock stationär und das Gehäuse drehbar. Bei der erstgenannten Alternative ist der Motor mit einer Antriebswelle verbunden. Bei der zweitgenannten Alternative ist der Motor mit einem Rad oder einer Seiltrommel für eine Winde oder dergleichen verbunden.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. In a heavy duty engine design, 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. Either the housing can be stationary and the cylinder block rotatable, or conversely the cylinder block stationary and the housing rotatable. In the former alternative, the motor is connected to a drive shaft. In the second alternative, the motor is connected to a wheel or a cable drum for a winch or the like.

Bei den bekannten Ausführungsformen von Motoren dieser Art wird die Kolbenkraft über eine pleuelstangenähnliche Kolbenstange auf die Rolle übertragen. Die Rolle ist in ihrer Mitte in einem Lager, das am äußeren Ende der Kolbenstange angeordnet ist, gelagert und mit Rollbahnen auf jeder Seite der Lagerung versehen. Die Kolbenstange ist an ihrem inneren Ende im Kolben gelagert. Die Länge der Rolle nimmt mit der Breite der Lagerung in der Stange zu. Die Breite der Rollbahn im Motorgehäuse wird um ein entsprechendes Maß breiter, während ihr mittlerer Teil unausgenutzt bleibt.In the known embodiments of engines of this type, 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.

Der Erfindung liegt die Aufgabe zugrunde, einen hydraulischen Radialkolbenmotor der eingangs genannten Art zu entwickeln, der einerseits sehr kompakt ist und kleine radiale und axiale Abmessungen hat, und bei dem andererseits die Breite der ganzen Nockenkurve als effektive Rollbahn ausgenutzt wird. Ferner soll erreicht werden, daß die Kraft in der Weise über das Druckmittel auf die Rolle übertragen wird, daß das Druckmittel direkt auf die Rolle wirkt, so daß die Beanspruchungen des die Rolle tragenden Lagers reduziert werden und folglich die Übertragung größerer Kräfte möglich ist und/oder die Lebensdauer der Verschleißteile vergrößert wird. Schließlich sollen Rollenhalter und Kolben so ausgebildet werden, daß Unvollkommenheiten in der Form sowie betriebsbedingte Verformungen der Motorbauteile keine schädlichen Beanspruchungen in oder zwischen Kolben und Rollenhalter sowie zwischen Rollenhalter und Rolle verursachen.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.

Zur Lösung dieser Aufgabe wird ein hydraulischer Radialkolbenmotor gemäß dem Oberbegriff des Anspruches 1 vorgeschlagen, der erfindungsgemäß die im kennzeichnenden Teil des Anspruches 1 genannten Merkmale hat.To solve this problem, a hydraulic radial piston motor is proposed according to the preamble of claim 1, which according to the invention has the features mentioned in the characterizing part of claim 1.

Vorteilhafte Ausgestaltungen der Erfindung sind in den weiteren Ansprüchen genannt.Advantageous embodiments of the invention are mentioned in the further claims.

Gemäß der Erfindung sind die in den Zylindern im Zylinderblock gleitenden Kolben an ihrem äußeren Ende mit einer sphärischen Lagerfläche versehen. Die an der Nockenkurve entlanglaufenden Rollen sind in Rollenhaltern mit einer zylindrischen Lagersitzfläche gelagert, die als hydrostatisches Lager ausgeführt und mit einer sphärischen Lagerfläche versehen-ist, die an der sphärischen Lagerfläche des Kolbens anliegt. Der Rollenhalter ist in allen Richtungen um das Zentrum des sphärischen Lagers kippbar. Dadurch, daß der Rollenhalter auf diese Weise relativ zum Kolben kippen kann, wird eine Beanspruchung des Kolbens durch Kippmomente vermieden, die auf Rollenhalterbewegungen beruhen, die durch Unvollkommenheiten der Nockenkurve und der Führungen der Rollen verursacht werden.According to the invention, 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.

Die Kolben des Motors haben eine durchgehende axiale Boh- . rung, die zweckmäßigerweise im äußeren Teil einen größeren Durchmesser als im inneren Teil hat. Die Rollenhalter, welche die Rollen tragen, haben einen Führungszapfen, der in den äußeren Teil der Bohrung mit dem größeren Durchmesser hineinragt. Um zu verhindern, daß die Rollenhalter und die Kolben beim Betrieb des Motors voneinander getrennt werden, können Rollenhalter und Kolben durch eine kräftige Feder zusammengehalten werden, die in dem genannten Führungszapfen-und am inneren Teil des Kolbens befestigt ist. Der Rollenhalter kann so ausgebildet sein, daß er die Rolle um mehr als 180° umfaßt, wodurch die Rolle im Halter fixiert wird. Der Rollenhalter kann jedoch auch mit einem kleineren Umschließungswinkel als 180°C ausgeführt sein, wobei der Rollenhalter oder der Motor mit anderen Vorrichtungen zur Fixierung einer Rolle im Rollenhalter oder zur Führung der Rolle versehen wird. Die zylindrische Lagersitzfläche für die Rolle wird mit einer abgegrenzten hydrostatischen Tragfläche versehen, so daß eine geeignete Ausbalancierung der auf die Rolle wirkenden Kraft erreicht wird. Die Tragfläche kann durch Nuten abgegrenzt sein, die eine Spaltdichtung bewirken. Die auf den Rollenhalter und den Kolben wirkenden radialen Druckkräfte werden hydrostatisch zu mehr als 80 %, vorzugsweise zu 85 bis 90 %, ausbalanciert.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. In order to prevent the roller holder and the piston from being separated from one another during operation of the engine, 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. However, 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%.

Anhand der Figuren soll die Erfindung näher erläutert werden. Es zeigen

  • Fig. 1 schematisch in einem Radialschnitt einen bekannten hydraulischen Motor der hier behandelten Art,
  • Fig. 2 einen Axialschnitt durch ein Ausführungsbeispiel eines Motors gemäß der Erfindung,
  • Fig. 3 die wesentlichen Teile des Ausführungsbeispiels gemäß Fig. 2 in Explosionsdarstellung,
  • Fig. 4 einen Schnitt durch ein Rollenlager senkrecht zur Lagerwelle,
  • Fig. 5 einen Schnitt durch einen Rollenhalter längs der Linie A-A in Fig. 4,
  • Fig. 6 eine Ansicht in Richtung B-B in Fig. 2 des Flachschiebers zur Steuerung des Druckmittelflusses zum Motor hin und vom Motor weg,
  • Fig. 7 einen Schnitt längs der Linie C-C in Fig. 6.
The invention will be explained in more detail with reference to the figures. Show it
  • 1 schematically in a radial section a known hydraulic motor of the type discussed here,
  • 2 shows an axial section through an embodiment of a motor according to the invention,
  • 3 shows the essential parts of the embodiment of FIG. 2 in an exploded view,
  • 4 shows a section through a roller bearing perpendicular to the bearing shaft,
  • 5 shows a section through a roll holder along the line AA in FIG. 4,
  • 6 shows a view in the direction BB in FIG. 2 of the flat slide for controlling the pressure medium flow towards the engine and away from the engine,
  • 7 shows a section along line CC in FIG. 6.

In Fig. 1 bezeichnet 1 eine Scheibe, deren innere Umfangswand als Nockenkurve 2 ausgebildet ist. Diese inwandige Nockenkurve ist in einem nicht dargestellten, drehbaren Gehäuse angeordnet, welches ein Rad oder eine Winde antreiben kann. Ein Zylinderblock 3 mit mehreren Zylindern 4 ist stationär angeordnet. Auf jeder Seite des Zylinderblockes 3 befinden sich als Scheiben ausgebildete Führungsglieder 5 mit Schlitzen 6 zur Führung der Rollen 7 und zur Aufnahme von Tangentialkräften, die auftreten, wenn die Rollen 7 gegen die Nockenkurve 2 gepreßt werden. Die Führungsglieder 5 sind fest mit dem Zylinderblock 3 verbunden und somit ebenfalls stationär. In den Zylindern gleiten Kolben 8. Diese sind mit den Rollen 7 über pleuelstangenähnliche Stangen 10 verbunden. Die Rollen sind mit ihrem mittleren Teil drehbar in einem nicht gezeigten, Lager am äußeren Ende der Stangen gelagert. In dem Zylinderblock 3 ist ein umlaufender Schieber 11 zur Verteilung von Druckmittel auf die Zylinder 4 angeordnet. Die voll dargestellten Druckleitungen und die daran gerade angeschlossenen Zylinder sind mit Druckmittel von hohem Druck gefüllt, während die übrigen nicht gefüllt sind, bzw. das in ihnen befindliche Druckmittel nicht unter Druck steht.In Fig. 1, 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.

In den übrigen Figuren bezeichnet 20 das Motorgehäuse eines hydraulischen Motors gemäß der Erfindung, wobei es sich um ein nicht rotierendes Motorgehäuse handelt. Dieses hat zwei Stirnwände 21 und 22 und eine zwischen diesen angebrachte Nockenscheibe 23 mit einer inwandigen Nockenkurve 24 (Fig. 3). Die Stirnwände 21 und 22 sowie die Nockenscheibe 23 werden von Bolzen 27 zusammengehalten. Ein Zylinderblock 25 mit einem Wellenzapfen 26 ist mittels Lagern 28, 30 und 31 rotierbar in den Stirnwänden 21 und 22 des Motorgehäuses 20 gelagert. Das Teil 32 des Zylinderblockes wird mit einer Kegelkupplung 33 an eine gezeigte Welle angeschlossen.In the remaining figures, 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.

Im Zylinderblock 25 befinden sich mehrere radial gerichtete Zylinder 34, in welchen Kolben 35 gleiten. Diese Kolben haben durchgehende Bohrungen 36, deren radial äußerer Teil 36a einen größeren Durchmesser als der übrige Teil der Bohrung 36 hat. Die Kolben sind an ihren radial äußeren Enden mit einer sphärischen, kugelzonenförmigen Lagersitzfläche 37 versehen. Antriebsrollen 38 laufen längs der Nockenkurve 24. Diese Antriebsrollen 38 sind in Rollenhaltern 40 gelagert, die wie hydrostatische Lager ausgebildet sind. Ferner sind diese Rollenhalter 40 mit einer der Lagersitzfläche 37 der Kolben 35 angepaßten, sphärischen, kugelzonenförmigen Lagersitzfläche 41 versehen. Die Rollenhalter 40 können somit in allen Richtungen im Verhältnis zu den Kolben 35 gekippt werden. Auf die Kolben wirken folglich weder Kippmomente noch Seitenkräfte. Die Rollenhalter 40 haben einen Führungszapfen 42, der in die Ausbohrung 36a hineinragt. Die Kolben 35 und die Rollenhalter 40 werden von einer Feder 43 zusammengehalten, die mit Stiften 44 und 45 in dem Führungszapfen 42 bzw. im Kolben 35 befestigt ist. Der Rollenhalter 40 umfaßt die Rolle 38 um mehr als 180°, wodurch die Rolle 38 in dem Halter 40 radial fixiert wird. Wegen dieser Umfassung besteht der Halter 40 aus zwei Teilen 40a und 40b, die mit Bolzen 46 zusammengehalten werden (Fig. 4).In the cylinder block 25 there are a plurality of radially directed cylinders 34, in which pistons 35 slide. These 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. Furthermore, these 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).

Die Rollen 38 sind mit Flanschen 47 zu ihrer Führung in axialer Richtung im Verhältnis zur Nockenscheibe 23 versehen. Ferner sind an den axialen Enden der Rollen Zapfen 48 vorhanden, welche Rollenlager tragen, deren Außenring . eine Führungsrolle 50 bildet. Die Lager sind mittels Unterlegscheiben 51 und Sicherungsringen 52 auf den Zapfen 48 fixiert. Zwei scheibenförmige Führungseinheiten 53 mit radial gerichteten Schlitzen 54 sind durch Bolzen 55 fest mit dem Zylinderblock 25 verbunden. Durch die Führungsrollen 50 werden auf die Rollen 38 wirkende Tangentialkräfte über die Führungseinheiten 53 auf den Zylinderblock 25 übertragen.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.

Druckmittel wird über einen Flachschieber mit zwei Schieberingen 56 und 57 zu den Zylindern 34 des Zylinderblocks 25 hin und von diesen weg geleitet. Der Ring 56 ist derart mit dem Zylinderblock verbunden, daß er mit diesem rotiert. Der Ring 57 ist mit der Stirnwand 22 derart verbunden, daß er nicht rotiert, jedoch axial im Verhältnis zum Ring 56 verschiebbar ist. Der Ring 56 hat durchgehende Löcher 58, die mitten vor Kanälen 60 im Zylinderblock 25 münden, welche Kanäle 60 zu den Zylindern führen. Der Ring 57 hat durchgehende Löcher 61, die mitten vor Kanälen 62 in der Stirnwand 22 für die Zufuhr bzw. Fortleitung von Druckmittel dienen. Das nach innen gerichtete Ende des Kanals 62 ist im Durchmesser weiter aufgebohrt, und in der so geschaffenen Ausbohrung 63 ist eine Hülse 64 angeordnet, die von einer Feder 65 und dem auf die innere Stirnfläche der Hülse wirkenden Druckmittel gegen den Schieberring 57 gepreßt wird. Im Schieberring 57 sind durchgehende Bohrungen 66 vorhanden mit einer im Durchmesser kleineren Öffnung 67 auf der dem Ring 55 zugewendeten Seite. In diesen Bohrlöchern 66 sind Kolben 68 angeordnet, die an der Stirnwand 22 anliegen. Diese Kolben haben die Aufgabe, einen Ausgleich von Kräften zu schaffen, die bei dem Wechsel zwischen Zufuhr und Fortleitung von Druckmittel zu bzw. von den Zylindern 34 auftreten.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. These pistons have the task of balancing forces which occur when changing between the supply and the discharge of pressure medium to and from the cylinders 34.

Die Kräfte zwischen den Kolben 35 und den Rollenhaltern 40 sowie die Kräfte zwischen den Rollen 38 und den Rollenhaltern 40 sind zum größten Teil hydrostatisch ausbalanciert.-Die Lagerdrücke auf die aneinander liegenden Lagerflächen 37 und 41 des Kolbens 35 bzw. Rollenhalters 40 sowie zwischen den Lagerflächen 69 des Rollenhalters und der Oberfläche der Rolle 38 sind klein. Das Druckmittel im Zylinder 34 hat durch die Bohrung 36 einen freien Zugang durch den Kolben 35 zum Raum 78 zwischen dem Kolben 35 und dem Halter 40. Im Rollenhalter 40 ist ein Kanal 70 angebracht, durch den das Druckmittel im Raum 78 Zugang zu der Vertiefung 71 in der Lagerfläche 69 des Rollenhalters 40 hat. Wie es am besten in den Figuren 4 und 5 gezeigt ist, wird diese Vertiefung von mindestens einer, vorzugsweise zwei ringförmigen Nuten 72 und 73 umgeben. Die Nut 72 steht über einen flachen Kanal 74 mit der Vertiefung 71 in Verbindung. Die Nut 73 und die an ihr angeschlossene, zur Seitenkante des Rollenhalters führende Nut 75 sind Dränierungsnuten, die Druckmittel ableiten, das zwischen der Rolle 38 und der zwischen den Nuten 72 und 73 vom Rollenhalter 40 gebildeten, ringförmigen Dichtungsfläche 76 hindurchdringt. Die Größe und die Breite der von den Nuten 72 und 73 begrenzten Dichtungsfläche 76 werden so groß gewählt, daß man die gewünschte hydrostatische Ausbalancierung der auf die Rolle 38 wirkenden, Kräfte und einen niedrigen Flächendruck auf die Dichtungsfläche 76 erhält. Bei gut ausgewogenem Flächendruck ist der Verlust an schmierendem Druckmittel, das die Dichtungsfläche 76 passiert, klein. Ferner verhindert die Dränierungsnut 73, daß das Druckmittel zu den äußeren Abschnitten des Rollenhalters gelangt und diesen in störender Weise deformiert. Dadurch, daß man den Bereich innerhalb der inneren Nut 72 ganz oder teilweise mit einer Vertiefung versieht, erhält man eine wohldefinierte Dichtungsfläche, die durch Verformungen des zentralen Bereichs des Rollenhalters aufgrund der Kolbenkraft nur unerheblich beeinflußt wird. Auch der Durchmesser der sphärischen, kugelzonenförmigen Lagerfläche 37 am Ende des Kolbens 35 und die mit dieser Lagerfläche 37 zusammenwirkende Lagerfläche 41 des Rollenhalters 40 werden mit Rücksicht auf die gewünschte hydrostatische Ausbalancierung bemessen.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. 4 and 5, 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. With a well-balanced surface pressure, 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. By providing the area within the inner groove 72 with a recess in whole or in part, 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.

Der Aufbau des Schieberringes 56 geht am besten aus den Figuren 6 und 7 hervor. Das Loch 61 ändert seine Form an der Seite, die an den Schieberring 57 gleitet, und hat hier eine langgestreckte, ovale Form.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.

Unter gewissen Betriebsbedingungen kann es vorkommen, daß bei dem Radialkolbenmotor gemäß der Erfindung der Rollenhalter(40) vom Kolben (35) abhebt. Um bei einem solchen Abheben einen größeren Druckmittelverlust zu vermeiden, wird gemäß der Erfindung ein Teil des Zapfens (42) mit einem solchen Durchmesser versehen, daß zwischen diesem Teil des Zapfens und der ihn umgebenden Bohrung im Kolben(35) ein Drosselspalt gebildet wird. Hierdurch wird erreicht, daß beim Auftreten eines Abhebens der Druckmittelverlust sehr klein gehalten wird.Under certain operating conditions it can happen that in the radial piston motor according to the invention the roller holder (40) lifts off the piston (35). In order to avoid a greater loss of pressure medium during such lifting, 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.

Claims (11)

1. Hydraulischer Radialkolbenmotor mit einem Gehäuse (20), das eine Nockenscheibe (23) mit einer inwandigen Nockenkurve (24) enthält, mit einem Zylinderblock (25), der mehrere radial gerichtete Zylinder (34) hat, mit in diesen Zylindern (34) gleitenden Kolben (35), mit Rollenhaltern (40), die eine zylindrische Lagerfläche haben, mit an der Nockenkurve (24) laufenden Rollen (38), mit Führungseinheiten (53), die mit dem Zylinderblock (25) des Motors fest verbunden sind und axial gerichtete Steuerschlitze (54) haben, und mit Wellenzapfen (48) an den Rollen (38), die Führungslager (50) tragen, die in den Schlitzen (54) in den Führungseinheiten (53) laufen und auf die Rollen (38) wirkende Tangentialkräfte auf die Führungseinheiten (53) und damit auf den Zylinderblock (25) übertragen, dadurch gekennzeichnet, daß die Rollenhalter (40) und die Kolben (35) separate Bauteile sind, die derart miteinander verbunden sind, daß Winkelbewegungen zwischen den Rollenhaltern (40) und den Kolben (35) in allen Richtungen möglich sind.1. Hydraulic radial piston motor with a housing (20), which contains a cam disk (23) with an in-wall cam curve (24), with a cylinder block (25), which has a plurality of radially directed cylinders (34), with in these cylinders (34) sliding piston (35), with roller holders (40) which have a cylindrical bearing surface, with rollers (38) running on the cam curve (24), with guide units (53) which are fixedly connected to the cylinder block (25) of the engine and have axially directed control slots (54) and with shaft journals (48) on the rollers (38) which carry guide bearings (50) which run in the slots (54) in the guide units (53) and act on the rollers (38) Transfer tangential forces to the guide units (53) and thus to the cylinder block (25), characterized in that the roller holders (40) and the pistons (35) are separate components which are connected to one another in such a way that angular movements between the roller holders (40) and the piston (35) in a all directions are possible. 2. Hydraulischer Motor nach Anspruch.1, dadurch gekennzeichnet, daß die Kolben (35) und die Rollenhalter (40) mit zur gegenseitigen Anlage bestimmten sphärischen, kugelzonenförmigen Lagerflächen (37, 41) versehen sind.2. Hydraulic motor according to Claim 1, characterized in that the pistons (35) and the roller holder (40) are provided with spherical, spherical-zone-shaped bearing surfaces (37, 41) intended for mutual contact. 3. Hydraulischer Motor nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die Kolben (35) des Motors eine durchgehende axiale Bohrung (36) aufweisen und daß die Rollenhalter (40) einen Führungszapfen (42) aufweisen, der in die Bohrung (36) in dem Kolben (35) hineinragt.3. Hydraulic motor according to claim 1 or 2, characterized in that the pistons (35) of the motor have a continuous axial bore (36) and that the roller holder (40) have a guide pin (42) which in the bore (36) protrudes into the piston (35). 4. Hydraulischer Motor nach Anspruch 3, dadurch gekennzeichnet, daß die Rollenhalter (40) mit hydrostatischen Lagern versehen sind, daß diese Lager über einen Kanal (70) in den Rollenhaltern (40) mit der Bohrung (36) in den Kolben (35) in Verbindung stehen, und daß über diese Verbindung Schmiermittel zuführbar ist.4. Hydraulic motor according to claim 3, characterized in that the roller holder (40) are provided with hydrostatic bearings, that these bearings via a channel (70) in the roller holders (40) with the bore (36) in the piston (35) are in communication, and that lubricant can be supplied via this connection. 5. Hydraulischer Motor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Rollenhalter (40) mit mindestens einer ringförmigen Nut (72, 73) versehen sind und daß der von dieser Nut eingeschlossene Bereich der Lagerfläche (69) des Rollenhalters mit einer Vertiefung (71) versehen ist.5. Hydraulic motor according to one of the preceding claims, characterized in that the roller holder (40) are provided with at least one annular groove (72, 73) and that the region of the bearing surface (69) of the roller holder enclosed by this groove with a recess ( 71) is provided. 6. Hydraulischer Motor nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß die Rollenhalter (40) mit einer ersten ringförmigen inneren Nut (72) und einer zwei-. ten ringförmigen äußeren Dränierungsnut (73) versehen sind, daß die von den beiden ringförmigen Nuten (72, 73) eingeschlossene ringförmige Fläche eine Dichtungsfläche (76) bildet und daß der von der ersten Nut (72) eingeschlossene Bereich der Lagerfläche (69) des Rollenhalters mit einer Vertiefung (71) versehen ist.6. Hydraulic motor according to one of claims 1 to 4, characterized in that the roller holder (40) with a first annular inner groove (72) and a two. th annular outer drainage groove (73) are provided that the annular surface enclosed by the two annular grooves (72, 73) forms a sealing surface (76) and that the region of the bearing surface (69) of the roll holder enclosed by the first groove (72) is provided with a recess (71). 7. Hydraulischer Motor nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß die Rollenhalter (40) in ihrem zentralen Bereich mit einer Vertiefung (71) und mit einer diese Vertiefung umgebenden Dränierungsnut (73) versehen sind und daß die von der Vertiefung (71) und der Dränierungsnut (73) begrenzte Fläche der Rollenhalter eine zur Anlage für die Rolle (38) bestimmte ringförmige Dichtungsfläche (76) bildet.7. Hydraulic motor according to one of claims 1 to 4, characterized in that the roller holder (40) are provided in their central region with a recess (71) and a drainage groove (73) surrounding this recess, and that of the recess ( 71) and the drainage groove (73) limited area of the roller holder forms an annular sealing surface (76) intended for bearing on the roller (38). 8. Hydraulischer Motor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Kolben (35) einerseits und die Rollenhalter (40) andererseits von einer in den Kolben (35) angeordneten Feder (43) zusammengehalten werden.8. Hydraulic motor according to one of the preceding claims, characterized in that the piston (35) on the one hand and the roller holder (40) on the other hand by a spring (43) arranged in the piston (35) are held together. 9. Hydraulischer Motor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Rollenhalter (40) mit dem hydrostatischen Lager (69) die an der Nockenkurve (24) entlanglaufende Fläche der Rolle (38) um mehr als 1800 umschließen.That the roller holder (40) with the hydrostatic bearing (69) by more than 180 0 enclose 9. A hydraulic motor according to one of the preceding claims, characterized in that the running along the cam curve (24) surface of the roller (38). 10. Hydraulischer Motor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die auf eine Rolle (38) wirkenden Kräfte in dem tragenden Lager (69) zu mindestens 80 % hydrostatisch ausbalanciert sind.1 0 . Hydraulic motor according to one of the preceding claims, characterized in that the forces acting on a roller (38) in the supporting bearing (69) are at least 80% hydrostatically balanced. 11. Hydraulischer Motor nach einem der Ansprüche 3 bis 10, dadurch gekennzeichnet, daß ein Teil des Führungszapfens (42) einen solchen Durchmesser hat, daß zwischen diesem Teil des Führungszapfens und der ihn umgebenden Bohrung (36a) des Kolbens (35) ein Drosselspalt gebildet wird, der einen größeren Druckmittelverlust beim Abheben des Kolbens (35) vom Rollenhalter (40) verhindert.11. Hydraulic motor according to one of claims 3 to 1 0 , characterized in that a part of the guide pin (42) has a diameter such that a throttle gap between this part of the guide pin and the surrounding bore (36 a) of the piston (35) is formed, which prevents a greater loss of pressure medium when lifting the piston (35) from the roller holder (40).
EP83710058A 1982-09-08 1983-08-31 Radial-piston hydraulic engine Expired EP0102915B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE8205097A SE456517B (en) 1982-09-08 1982-09-08 HYDRAULIC RADIAL PISTON ENGINE
SE8205097 1982-09-08

Publications (3)

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

Family

ID=20347753

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83710058A Expired EP0102915B1 (en) 1982-09-08 1983-08-31 Radial-piston hydraulic engine

Country Status (5)

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

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0524437A1 (en) * 1991-06-25 1993-01-27 Hägglunds Denison Drives Ab Hydraulic piston motor
DE19816452B4 (en) * 1997-04-10 2010-06-10 Hägglunds Drives AB Piston for a hydraulic motor
WO2012159725A1 (en) * 2011-05-23 2012-11-29 Robert Bosch Gmbh Hydrostatic radial piston machine and piston for a hydrostatic radial piston machine
FR3010741A1 (en) * 2013-09-18 2015-03-20 Poclain Hydraulics Ind CARTRIDGE FORMING MOTOR OR HYDRAULIC PUMP PREASSEMBLING WITH RADIAL PISTONS

Families Citing this family (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FI73789C (en) * 1983-12-07 1987-11-09 Partek Ab HYDRAULISK MOTOR.
DE3531632A1 (en) * 1985-09-05 1987-03-12 Rexroth Mannesmann Gmbh RADIAL PISTON MACHINE
US4974496A (en) * 1986-07-23 1990-12-04 Sea Shelf Engineering Pty. Ltd. A hydrocyclic motor
IT1221428B (en) * 1988-05-18 1990-07-06 Corghi Elettromecc Spa MULTI-CYLINDER CONTROL UNIT, FLUID OPERATED, PARTICULARLY SUITABLE FOR TIRE CHANGING MACHINES
AUPN840796A0 (en) * 1996-03-01 1996-03-28 Raffaele, Peter Fluid machines
CN2284883Y (en) * 1996-07-12 1998-06-24 陈智 Full rolling moving gear
US5996324A (en) * 1998-01-22 1999-12-07 Case Corporation Hydraulic feeder reverser
DE19832696A1 (en) * 1998-07-21 2000-01-27 Mannesmann Rexroth Ag Radial piston machine with roller guides, with one of two roller guides for one roller fixed directly, without auxiliary parts, to the cylinder block so that it cannot rotate
FR2834011B1 (en) * 2001-12-24 2004-03-19 Poclain Hydraulics Ind RADIAL PISTON HYDRAULIC MOTOR
FR2834012B1 (en) * 2001-12-24 2004-03-19 Poclain Hydraulics Ind RADIAL PISTON HYDRAULIC MOTOR
ITMO20020287A1 (en) * 2002-10-02 2004-04-03 I Societa Apparecchiature Idra Uliche Spa Sa HYDRAULIC MACHINE WITH HIGH PERFORMANCE RADIAL CYLINDERS.
EP1557562B1 (en) * 2004-01-23 2009-06-17 Manfreda, Marija Distributing system for a piston hydraulic engine
CN100387832C (en) * 2005-09-07 2008-05-14 周沛凝 Low speed great torque hydraulic drive mechanism
DE102006058076A1 (en) * 2006-12-07 2008-06-19 Zf Friedrichshafen Ag Hydraulic radial piston motor
EP2232068B1 (en) * 2007-12-21 2017-11-08 Carleton Life Support Systems, Inc. Radial cam-driven compressor and cam-driven compressor assemblies
FR2955903B1 (en) * 2010-02-01 2012-03-16 Poclain Hydraulics Ind HYDROBASE-FORMING SUBASSEMBLY FOR HYDRAULIC ENGINES AND METHOD OF ASSEMBLY
DE102012008623A1 (en) 2012-04-28 2013-10-31 Robert Bosch Gmbh Radial piston engine
DE102013217714A1 (en) 2013-09-05 2015-03-05 Robert Bosch Gmbh Hydrostatic radial piston machine
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
DE102016214978A1 (en) 2016-08-11 2018-02-15 Robert Bosch Gmbh Hydrostatic radial piston machine
DE102016214967A1 (en) 2016-08-11 2018-02-15 Robert Bosch Gmbh Hydrostatic radial piston machine
DE102016214976A1 (en) 2016-08-11 2018-02-15 Robert Bosch Gmbh Hydrostatic radial piston machine and method of operating a hydrostatic radial piston machine
US10400817B2 (en) 2016-11-22 2019-09-03 Woodward, Inc. Radial bearing device
EP3511568B1 (en) 2018-01-10 2022-03-23 Robert Bosch GmbH Shaft seal arrangement and radial piston machine
FR3128692A1 (en) * 2021-10-29 2023-05-05 Safran Landing Systems Device for driving a wheel in rotation comprising a hydraulic motor with radial pistons and means for locking the pistons in the retracted position.

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB526782A (en) * 1939-04-24 1940-09-25 Walter Ernst Improvements in or relating to rotary radial hydraulic pumps or motors
GB864767A (en) * 1959-04-14 1961-04-06 Wadefelt Carl I Improvements in rotary engines
CH390689A (en) * 1961-02-09 1965-04-15 Hydrel Ag Infinitely variable hydraulic machine that can be used as a pump or motor
GB1125561A (en) * 1964-09-02 1968-08-28 British Aircraft Corp Ltd Improvements in hydraulic motors and pumps
FR2033554A5 (en) * 1969-02-27 1970-12-04 Pr Motors Ltd

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB175914A (en) * 1921-04-06 1922-03-02 Rankin Kennedy Mcalister Improved multiple cylinder engine
DE906766C (en) * 1943-07-16 1954-03-18 Hans Thoma Dr Ing Piston for axial piston gear
US2638850A (en) * 1952-01-24 1953-05-19 Ferris Walter Piston assembly for axial type hydrodynamic machines
US2980077A (en) * 1959-03-17 1961-04-18 English Electric Co Ltd Hydraulic devices
US3165068A (en) * 1960-06-27 1965-01-12 American Brake Shoe Co Fluid power apparatus
FR1347220A (en) * 1962-11-16 1963-12-27 Hydraulic device for transforming energy at variable speed
GB1180513A (en) * 1968-05-23 1970-02-04 Cam Rotors Ltd Radial Piston Fluid Pressure Motor
US3789741A (en) * 1971-07-26 1974-02-05 Fmc Corp Hydrostatic bearing for radial piston pump
GB1463495A (en) * 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

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB526782A (en) * 1939-04-24 1940-09-25 Walter Ernst Improvements in or relating to rotary radial hydraulic pumps or motors
GB864767A (en) * 1959-04-14 1961-04-06 Wadefelt Carl I Improvements in rotary engines
CH390689A (en) * 1961-02-09 1965-04-15 Hydrel Ag Infinitely variable hydraulic machine that can be used as a pump or motor
GB1125561A (en) * 1964-09-02 1968-08-28 British Aircraft Corp Ltd Improvements in hydraulic motors and pumps
FR2033554A5 (en) * 1969-02-27 1970-12-04 Pr Motors Ltd

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0524437A1 (en) * 1991-06-25 1993-01-27 Hägglunds Denison Drives Ab Hydraulic piston motor
DE19816452B4 (en) * 1997-04-10 2010-06-10 Hägglunds Drives AB Piston for a hydraulic motor
WO2012159725A1 (en) * 2011-05-23 2012-11-29 Robert Bosch Gmbh Hydrostatic radial piston machine and piston for a hydrostatic radial piston machine
FR3010741A1 (en) * 2013-09-18 2015-03-20 Poclain Hydraulics Ind CARTRIDGE FORMING MOTOR OR HYDRAULIC PUMP PREASSEMBLING WITH RADIAL PISTONS

Also Published As

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

Similar Documents

Publication Publication Date Title
EP0102915A2 (en) Radial-piston hydraulic engine
EP0220175B1 (en) Axial-piston hydraulic pump with inclined thrust plate
EP0044070A1 (en) Axial piston pump with two delivery streams
DE2533498A1 (en) CONTROL SYSTEM FOR AN AXIAL PISTON MACHINE FOR TRANSFER OF FLOW ENERGY
EP0620358A1 (en) Hydraulic motor
DE2736581A1 (en) FRICTION GEAR
DE2947553C2 (en) Bearing of the drive shaft of an axial piston machine in bent axis design
DE69905554T2 (en) SEALING ARRANGEMENT FOR DISC BRAKES
EP0728945B1 (en) Axial piston machine
DE3889122T2 (en) SELF-LOADING BENDING ADJUSTING ROLLER.
DE69211238T2 (en) Liquid piston engine
DE3800031A1 (en) Axial piston machine developing torque on the cam plate
DE1728310A1 (en) Pressure medium transmission device
DE2513549C3 (en) Axial piston machine with a swiveling, rotating cylinder drum
DE2351856C3 (en)
DE69418620T2 (en) RADIAL BEARING WITH SLIDE SHOE AND SLIDE SHOE FOR A RADIAL BEARING
DE2359734B1 (en) Hydrostatic piston engine
DE3033939C2 (en) Conical pulley for continuously adjustable conical pulley belt drive
DE2248316C2 (en) Radial piston machine
DE666542C (en) Friction gear change transmission, especially for motor vehicles
DE10028336C1 (en) Engine with axial piston has through guide channel between at least one tooth crown surface and tooth space bottom opposite it
DE2604455A1 (en) PISTON PUMP
DE19602770C2 (en) Piston roller guide for radial piston unit
DE1226418B (en) Device for pressing the angularly movable piston sliding blocks against the swash plate or swash plate of an axial piston machine (pump or motor)
DE3522037A1 (en) Hydrodynamic sliding bearing arrangement with automatic adaptation to the respective operating state

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

AK Designated contracting states

Designated state(s): BE DE FR GB IT LU NL

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Designated state(s): BE DE FR GB IT LU NL

17P Request for examination filed

Effective date: 19850510

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): BE DE FR GB IT LU NL

REF Corresponds to:

Ref document number: 3371550

Country of ref document: DE

Date of ref document: 19870619

ITF It: translation for a ep patent filed
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
ITTA It: last paid annual fee
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19920807

Year of fee payment: 10

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

Ref country code: GB

Payment date: 19920824

Year of fee payment: 10

Ref country code: DE

Payment date: 19920824

Year of fee payment: 10

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

Ref country code: NL

Payment date: 19920831

Year of fee payment: 10

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

Ref country code: LU

Payment date: 19920903

Year of fee payment: 10

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

Ref country code: BE

Payment date: 19920930

Year of fee payment: 10

EPTA Lu: last paid annual fee
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

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

Effective date: 19930831

Ref country code: GB

Effective date: 19930831

Ref country code: BE

Effective date: 19930831

BERE Be: lapsed

Owner name: A.B. HAGGLUND & SONER

Effective date: 19930831

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

Ref country code: NL

Effective date: 19940301

NLV4 Nl: lapsed or anulled due to non-payment of the annual fee
GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19930831

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

Ref country code: FR

Effective date: 19940429

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

Ref country code: DE

Effective date: 19940503

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST