EP0102915B1 - Radial-piston hydraulic engine - Google Patents

Radial-piston hydraulic engine 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
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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
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German (de)
French (fr)
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EP0102915A3 (en
EP0102915A2 (en
Inventor
Einar Samuelsson
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Hagglund and Soner AB
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Hagglund and Soner AB
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Publication of EP0102915A2 publication Critical patent/EP0102915A2/en
Publication of EP0102915A3 publication Critical patent/EP0102915A3/en
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03CPOSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00Reciprocating-piston liquid engines
    • F03C1/02Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0403Details, component parts specially adapted of such engines
    • F03C1/0428Supporting and guiding means for the pistons
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03CPOSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00Reciprocating-piston liquid engines
    • F03C1/02Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/047Reciprocating-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.

Description

Die vorliegende Erfindung betrifft einen hydraulischen Radialkolbenmotor gemäss dem Oberbegriff des Anspruches 1. Ein solcher Radialkolbenmotor ist bekannt aus der GB-A 864767.The present invention relates to a hydraulic radial piston motor according to the preamble of claim 1. Such a radial piston motor is known from GB-A 864767.

Motoren der vorgenannten Art enthalten 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 Zylinderblockvorhanden sind. Bei einerAusführung 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 derZylinderblock 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.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. 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 are arranged. The housing can either 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 einer bekannten Ausführungsform von Motoren der vorgenannten 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 mittlererTeil unausgenutzt bleibt.In a known embodiment of engines of the aforementioned type, 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.

Bei dem aus der GB-A 864767 bekannten Radialkolbenmotor ist am radial äusseren Ende des Kolbens ein Kreuzkopf befestigt, und an jedem Ende des Kreuzkopfes sind je zwei Lagerstellen vorhanden, von denen die weiter innen gelegene eine gegen eine Nockenkurve anliegende Rolle trägt und die äussere mittels eines Rollenlagers in einem radialen Schlitz geführt wird. Die Befestigung zwischen dem Kreuzkopf (Rollenhalter) und dem Kolben erfolgt über sphärische Flächen, die eine Winkelbewegung des Rollenhalters relativ zum Kolben erlauben. Nachteilig bei dieser bekannten Konstruktion ist neben der relativ grossen axialen Erstreckung die Durchbiegung des Rollenhalters in seiner Längsrichtung. Der Rollenhalter ist wie ein an beiden Enden eingespannter Träger angeordnet, auf den in der Mitte die Kraft vom Kolben wirkt. Hierdurch wird eine Durchbiegung verursacht, die zu einer wechselnden Belastung von Rollen und Rollenhalter führt, was einen vorzeitigen Verschleiss zur Folge hat.In the radial piston motor known from GB-A 864767, 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.

Aus der FR-A 2033554 ist ein Radialkolbenmotor bekannt, bei dem die Rollen unmittelbar in zylinderschalenförmigen Vertiefungen an den radial äusseren Stirnflächen der Kolben liegen. Ein zusätzlicher Rollenhalter ist hier also nicht vorhanden. Die Schmierung der genannten Lagerung erfolgt durch eine Bohrung durch den Kolben, wodurch gleichzeitig ein gewisses hydrostatisches Tragen der Rolle stattfindet. Dieses Ausführungsform hat den Nachteil, dass die unmittelbar am Zylinder ausgebildeten Lager auch die Tangentialkräfte aufnehmen müssen. Aus diesem Grunde muss der Kolben ein relativ grosses Spiel im Zylinder haben und darf nur mit einem einzigen Zylinderring gegenüber der Zylinderwand abdichten. Die Konstruktion hat eine relativ starke seitliche Belastung des Lagers und der Kolben-Zylinderführung zur Folge.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.

Der Erfindung liegt die Aufgabe zugrunde, einen hydraulischen Radialkolbenmotor der eingangs genannten Art zu entwickeln, bei dem die Lagerung, die Kolben-Zylinderführung und der Rollenhalter relativ geringen mechanischen Beanspruchungen ausgesetzt sind, insbesondere schädliche Beanspruchungen in oder zwischen Kolben und Rollenhalter sowie zwischen Rollenhalter und Rolle vermieden werden. Gleichzeitig soll der Radialkolbenmotor sehr kompakt sein und möglichst kleine radiale und axiale Abmessungen haben.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. At the same time, the radial piston motor should be very compact and have the smallest possible radial and axial dimensions.

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 können die in den Zylindern im Zylinderblock gleitenden Kolben an ihren äusseren Enden mit einer sphärischen Lagerfläche versehen sein, die mit einer entsprechenden Lagerfläche eines Rollenhalters zusammenwirkt, ohne dass hierdurch Biegemomente im Rollenhalter entstehen können. Dies wird dadurch erreicht, dass die an der Nockenkurve entlanglaufenden Rollen unmittelbar mit einer zylindrischen Lagersitzfläche in den Rollenhaltern gelagert sind, wobei dieses Lager als hydrostatisches Lager ausgebildet ist. Dank der sphärischen Lagerung des Rollenhalters auf der Stirnseite des Kolbens ist der Rollenhalter in allen Richtungen um das Zentrum des sphärischen Lagers kippbar, so dass eine Beanspruchung des Kolbens durch Kippmomente vermieden wird.According to the invention, 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.

Die Kolben des Motors haben eine durchgehende axiale Bohrung, 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, 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. In order to prevent the roller holder and the piston from being separated from one another when the engine is operating, 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. However, 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%.

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 according to 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 augebildet 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 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. The roles of the 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.

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 nicht 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, not shown, with a conical 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 roller holder 40 can thus be tilted in all directions 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, 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.

Druckmittel wird über einen Flachschieber mit zwei Schieberingen 56 und 57 zu den Zylindern 34 des Zylinderblocks 25 hin und von diesem 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 Druckmitel 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 56 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 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. 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 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. 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 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. 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, 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.

Claims (12)

1. Radial-piston hydraulic motor with a housing (20) comprising a cam disc (23) with an internal cam surface (24), with a cylinder block (25) comprising a plurality of radially extending cylinders (34), with pistons (35) slidably arranged in said cylinders (34), with roller holders (40) having a cylindrical bearing surface, with rollers (38) running along said cam surface (24), with guide units (53) being fixedly joined to said cylinder block (25) of the motor and being provided with axially extending guide slots (54), and with shaft pins (48) on the rollers (38) which shaft pins support guide bearings (50) running in the slots (54) in the guide units (53) and transmitting tangential forces, acting on the rollers (38), to said guide units (53) and thereby to the cylinder block (25), the roller holders (40) and the pistons (35) being separate components which are connected in such way that angular motions between the roller holders (40) and the pistons (35) are possible in all directions, characterized in that the rollers (38), with there central portion of there axial extension bear against the cam surface (24) and that the rollers (38) are hydrostatically journalled in there respective roller holders (40).
2. Radial-piston hydraulic motor according to claim 1, characterized in that the piston (35) and the roller holders (40) are provided with spherical-zone-shaped bearing surfaces (37, 41) destined for mutual abutment.
3. Radial-piston hydraulic motor according to any of claims 1 or 2, characterized in that the pistons (35) of the motor are provided with a through-going axial bore (36) and that the roller holders (40) are provided with a guide pivot (42) extending into said bore (36) in the respective piston (35).
4. Radial-piston hydraulic motor according to any of the preceding claims, characterized in that the hydrostatic bearings communicate with the bore (36) in the piston via a channel (70) in the respective roller holder (40) and that lubricant can be supplied via this connection.
5. Radial-piston hydraulic motor according to any of the preceding claims, characterized in that the forces exerted from the roller holder (40) on the respective piston (38) are hydrostatically balanced at least for the most part.
6. Radial-piston hydraulic motor according to any of the preceding claims, characterized in that the roller holders (40) are provided with at least one annular groove (72, 73) and that the area of the bearing surface (69) of the roller holder surrounded by said groove is provided with a recess (71).
7. Radial-piston hydraulic motor according to any of claims 1 to 5, characterized in that the roller holders (40) are provided with a first annular inner groove (72) and a second annular outer draining groove (73), that the annular surface confined by said two annular grooves (72, 73) forms a sealing surface (76), and that the area of the bearing surface (69) of the roller holder which is surrounded by said first groove (72) is provided with a recess (71).
8. Radial-piston hydraulic motor according to any of claims 1 to 5, characterized in that the roller holders (40), in there central region, are provided with a recess (71) and with a draining groove (73) surrounding said recess and that the area of the roller holder confined by said recess (71) and said draining groove (73) forms an annular sealing surface (76) destined for the abutment of the roller (38).
9. Radial-piston hydraulic motor according to any of the preceding claims, characterized in that the piston (35) on the one hand and the roller holders (40) on the other hand are held together by a spring (36) arranged in the piston (35).
10. Radial-piston hydraulic motor according to any of the preceding claims, characterized in that the roller holders (40) with the hydrostatic bearing (69) surrounds the surface of the roller (38) which runs along the cam surface (24) by more than 180 degree.
11. Radial-piston hydraulic motor according to any of the preceding claims, characterized in that the forces exerted on a roller (38) in the respective bearing (69) are hydrostatically counterbalanced to at least 80 per cent.
12. Radial-piston hydraulic motor according to any of claims 3 to 11, characterized in that a part of the guide pivot (42) has such a diameter that a throttling gap is formed between this part of the guiding pivot and the surrounding bore (36a) the piston, which throttling gap prevents any greater loss of pressure medium on occurrence of a lifting of 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)

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

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EP83710058A Expired EP0102915B1 (en) 1982-09-08 1983-08-31 Radial-piston hydraulic engine

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

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DE102016214976A1 (en) 2016-08-11 2018-02-15 Robert Bosch Gmbh Hydrostatic radial piston machine and method of operating a hydrostatic radial piston machine
DE102016214978A1 (en) 2016-08-11 2018-02-15 Robert Bosch Gmbh Hydrostatic radial piston machine
EP3511568A1 (en) 2018-01-10 2019-07-17 Robert Bosch GmbH Shaft seal arrangement and radial piston machine

Also Published As

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

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