EP0220175B1 - Axial-piston hydraulic pump with inclined thrust plate - Google Patents

Axial-piston hydraulic pump with inclined thrust plate Download PDF

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Publication number
EP0220175B1
EP0220175B1 EP85902965A EP85902965A EP0220175B1 EP 0220175 B1 EP0220175 B1 EP 0220175B1 EP 85902965 A EP85902965 A EP 85902965A EP 85902965 A EP85902965 A EP 85902965A EP 0220175 B1 EP0220175 B1 EP 0220175B1
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EP
European Patent Office
Prior art keywords
drum
bearing
force
cylinder
cylinder drum
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Expired
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EP85902965A
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German (de)
French (fr)
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EP0220175A1 (en
Inventor
Ingo Valentin
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Individual
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Individual
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Priority to AT85902965T priority Critical patent/ATE35719T1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2064—Housings
    • F04B1/2071—Bearings for cylinder barrels

Definitions

  • the invention relates to a hydraulic swash plate axial piston machine with a cylinder drum and pistons arranged in the cylinders of the cylinder drum, the piston heads of which are supported against the swash plate, while the cylinder drum is supported axially on a control mirror, the piston heads being adjacent to the useful torque related to the drum axis the cylinder drum also generate a radially acting drum shear force with a force application point lying in the drum axis, which shear force is absorbed by a bearing supporting the cylinder drum in the region of the drum shear force on the machine housing.
  • the cylinder drum has a collar on its outer circumference, which protrudes axially over the drum end face in the direction of the swash plate up to the plane perpendicular to the drum axis and intersecting the point of application of the drum transverse force.
  • the bearing supporting the cylinder drum in the form of a hydrodynamic plain bearing with cylindrical bearing surfaces. Thanks to this collar, the storage level, i. H.
  • the drum axis intersect directly in the area of the point of application of the drum lateral force, so that the support of the drum cylinder by the bearing also takes effect here, although the point of application of the drum lateral force in the plane running parallel to the swashplate through the centers of the piston heads and thus axially outside of the cylinder drum lies significantly in front of its face facing the swash plate.
  • the advantage of this drum bearing is that the drum shear force is unable to exert a tilting moment on the cylinder drum, which could result in a disturbing tilting of the cylinder drum on the control surface of a control disk, which controls the supply and discharge of the pressure medium to the cylinders of the cylinder drum and at which End face of the cylinder drum facing away from the swash plate, forming gap seals.
  • the collar and the bearing must include the swash plate and the row of piston sliding shoes that support the piston heads on the swash plate, which is undesirably large in the radial and axial direction and overall, also with regard to the pivotability of the Swashplate, complex constructions and due to the large diameter a greater loss of friction.
  • a swash plate axial piston machine which is provided as a double-acting arrangement with two swash plates, which face each other on both sides of the drum.
  • the pistons engaging the swash plates in pairs in the opposite direction are each arranged in common cylinders.
  • the pressure medium supply or discharge from the cylinder space is not possible from the front side of the drum, but takes place via pressure medium lines which open in the axial direction approximately in the middle of the cylinders and run radially there.
  • the cylinder drum In order to create the space required for this, the cylinder drum must have a correspondingly larger diameter, which leads to an undesirably large design in the radial direction and thus causes increased friction losses due to the large diameter.
  • the cylinder drum is supported by two bearings each approximately in the area of their end faces. Since the drum lateral forces act between the two bearings, tilting moments on the cylinder drum are safely absorbed. However, the second bearing causes further friction losses; In addition, the storage of the cylinder drum is determined in any case if its storage on the control mirror is also taken into account.
  • the cylinder drum also has a collar which projects axially over the end face of the drum in the direction of the swash plate up to the plane intersecting the point of application of the drum transverse force.
  • the collar is arranged on the inside here, that is to say in the region near the axis. As a result, the collar protrudes right up to the swashplate, which makes it difficult or even impossible to pivot. Therefore, the adjustability of the swash plate is not provided in this axial piston machine.
  • FR-A-1 599630 and FR-A-2115902 describe axial piston machines in which the cylinder drum is axially mounted approximately in the middle. The radial shear force acting on the drum therefore acts outside the bearing area and thus leads to an undesired tilting moment of the cylinder drum.
  • the object of the invention is to arrange and design the bearing of the cylinder drum in an axial piston machine of the type mentioned at the outset in such a way that even without an external encirclement of the swash plate and the piston sliding shoes, the cylinder drum is not supported by collars and bearings, and none on the cylinder drum or only causes tilting moments of such a small size that these residual moments can be absorbed by the control disk without disadvantage.
  • the plane of the bearing ie the plane of the bearing circle
  • the line of action of the resultants of all of them standing vertically on the guideway of the bearing Bearing forces include an acute angle with the drum axis and intersects the drum axis in the area of the point of application of the drum lateral force.
  • the bearing forces perpendicular to the guideway lie in the lateral surface of a cone, the tip of which can be thought of as the point of application of the individual bearing forces.
  • the base circle of the cone is formed by the bearing circle of the bearing and the cone tip lying in the drum axis either coincides with the point of application of the drum transverse force or is so close to it that the small distance between the drum transverse force and the resulting bearing force does not cause any disruptive tilting moments on the cylinder drum creates.
  • the height of the cone between the tip of the cone and the base circle of the cone is equal to the amount by which the bearing plane can be axially displaced away from the point of application of the drum transverse force towards the cylinder drum without the point of application of the resulting bearing force on the drum axis shifting accordingly and from the point of application of the Drum shear force removed.
  • the bearing itself can be moved axially far enough from the point of application of the drum lateral force and from the swash plate to the cylinder drum that it is axially far in front of the swash plate and in the area of the cylinder drum itself, and that therefore the bearing no longer needs to enclose the swash plate radially on the outside and also no longer a collar supporting the bearing is needed because the bearing can sit directly on the cylinder drum itself.
  • This enables small axial and radial dimensions and overall less construction and construction effort.
  • a preferred embodiment of the invention is characterized in that the guideway is formed by a conical ring surface, the cone tip of which lies in the drum axis on the same side of the force application point of the drum transverse force as the cylinder drum and which is so wide that the point of application of the drum transverse force is inside or at least tight next to the projection of the conical ring surface in the direction of its surface normal on the drum axis.
  • the conical ring surface should therefore be at least so wide that its projection onto the drum axis in any case includes the aforementioned periodic axial displacement of the point of application of the drum transverse force on the drum axis. Then each bearing support force applied in this point of attack always passes through the conical ring surface of the bearing.
  • the bearing can be designed as a hydrodynamically or hydrostatically acting slide bearing or as a tapered roller bearing.
  • the axial piston machines shown in the figures have a cylinder drum 2 connected to a shaft 1 and pistons 4 arranged in the cylinders 3.
  • the piston heads 5 are supported by sliding shoes 6 on the sliding surface of a swash plate 7, which is adjustable in the machine housing 8 with respect to its angle of inclination .
  • shaft 1 is a drive shaft in the case of a pump and an output shaft in the case of a motor. It is mounted in the machine housing 8 by means of a bearing 11.
  • the cylinder drum 2 is supported on the machine housing 8 in a further bearing 12.
  • the plane 13 of this bearing 12 intersects the drum axis 9 at a distance from the point of application 10 of the drum transverse force PkRes on the side of the cylinder drum 2.
  • the line of action 14 of the resulting bearing forces perpendicular to the guideway 15 of the bearing 12 forms an acute angle 26 with the drum axis 9 and cuts the drum axis 9 in the area of the point of application 10 of the drum lateral force PkRes.
  • the angle 26 is greater than approximately 60 °.
  • the bearing 12 can, as shown in FIG. 1 a, be a ball bearing, wherein the guideway 15 can be narrowed to a linear contact between the row of balls 16 on the one hand and the ball raceways 17 on the other. But mostly the guideway 15 will be formed by a conical ring surface, as shown in FIGS. 1, 2 and 3.
  • the conical tip 18 of this conical ring surface lies in the drum axis 9 on the same side of the force application point 10 as the cylinder drum 2.
  • the conical ring surface is otherwise so wide that the application point 10 of the drum transverse force PkRes within the projection of the conical in FIG Ring surface lies in the direction of its surface normal 19 on the drum axis 9.
  • the bearing 12 can be designed as a hydrodynamically or hydrostatically acting slide bearing, as shown in the figures in the right half of the figure, or as a tapered roller bearing, as shown in the figures on the left.
  • the bearing 12 is arranged directly between the outer peripheral surface 20 of the cylinder drum 2 and the housing jacket 2 of the machine housing 8 in the region of the end face 22 of the cylinder drum 2 facing the swash plate 7.
  • 2 and 3 show the case where the machine housing 8 has a pin 23, which is fixed to the machine housing and coaxial to the drum axis 9, between which and the cylinder drum 2 the bearing 12 is arranged.
  • the hollow pin 23 protrudes from the lower part of the machine housing 8 through the swash plate 7 to the cylinder drum 2 and receives the shaft 1.
  • the pin 23 arranged opposite to FIG. 2 engages through a central bore in the cylinder drum 2.
  • the cylinder drum 2 lies on its end face of the control surface facing away from the swash plate 7 of a control disc that controls the supply and removal of the conveying means to the cylinders 3 24 on. The supply and discharge of the funding takes place at the connections 25.

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

Abstract

The pump comprises a cylinder drum (20 converted to a shaft (1) and equipped with pistons (4) fitted in cylinders (3). The piston heads press against the oscillating plate (7) in such a way that the forces of the pistons do not produce only a useful torque on the cylinder drum (2), but also a radial transverse force (PK Res), the application point of which (10) is located in the axis of the shaft (1). The plane (13) of a bearing (12) supporting the drum (2) on the housing (8) intersects the axis (9) of the drum (1) at a certain distance from application point (10) of the transverse drum force (PKRes) on the side of the drum (2). The straight line (14) resulting from all the bearing forces acting perpendicularly on the guide path (15) of the bearing (12) forms a sharp angle (26) with the drum axis (9) and intersects the latter practically at the point of application (10) of the transverse force (PK Res), so that the bearing pressure of the drum takes effect in the region of this application point (10) and unwanted overturning torques acting on the drum are avoided.

Description

Die Erfindung betrifft eine hydraulische Schiefscheiben-Axialkolbenmaschine mit einer Zylindertrommel und in den Zylindern der Zylindertrommel angeordneten Kolben, deren Kolbenköpfe gegen die Schiefscheibe abgestützt sind, während die Zylindertrommel axial auf einem Steuerspiegel abgestützt ist, wobei die Kolbenköpfe neben dem auf die Trommelachse bezogenen nützlichen Drehmoment an der Zylindertrommel auch eine radial wirkende Trommelquerkraft mit in der Trommelachse liegendem Kraftangriffspunkt erzeugen, welche Querkraft von einem die Zylindertrommel im Bereich der Trommelquerkraft am Maschinengehäuse abstützenden Lager aufgenommen wird.The invention relates to a hydraulic swash plate axial piston machine with a cylinder drum and pistons arranged in the cylinders of the cylinder drum, the piston heads of which are supported against the swash plate, while the cylinder drum is supported axially on a control mirror, the piston heads being adjacent to the useful torque related to the drum axis the cylinder drum also generate a radially acting drum shear force with a force application point lying in the drum axis, which shear force is absorbed by a bearing supporting the cylinder drum in the region of the drum shear force on the machine housing.

Bei einer aus der Praxis bekannten Maschine dieser Art besitzt die Zylindertrommel an ihrem äusseren Umfang einen Kragen, der über die Trommelstirnseite in Richtung zur Schiefscheibe axial bis über die zur Trommelachse senkrechte, den Angriffspunkt der Trommelquerkraft schneidende Ebene vorsteht. Zwischen dem Kragen und dem äusseren Gehäusemantel des Maschinengehäuses befindet sich das die Zylindertrommel abstützende Lager in Form eines hydrodynamischen Gleitlagers mit zylindrischen Lagerflächen. Dank dieses Kragens kann die Lagerebene, d. h. die Ebene des Lagerkreises, die Trommelachse unmittelbar im Bereich des Angriffspunktes der Trommelquerkraft schneiden, so dass hier auch die Abstützung des Trommelzylinders durch das Lager wirksam wird, obwohl der Angriffspunkt der Trommelquerkraft in der parallel zur Schiefscheibe durch die Mitten der Kolbenköpfe verlaufenden Ebene und damit axial ausserhalb der Zylindertrommel erheblich vor ihrer der Schiefscheibe zugewandten Stirnseite liegt. Der Vorteil dieser Trommellagerung besteht darin, dass die Trommelquerkraft keine Kippmomente auf die Zylindertrommel auszuüben vermag, was ein störendes Kippen der Zylindertrommel auf der Steuerfläche einer Steuerscheibe ergeben könnte, welche die Zu- und Abfuhr des Druckmittels zu den Zylindern der Zylindertrommel steuert und an der der Schiefscheibe abgewandten Stirnfläche der Zylindertrommel unter Bildung von Spaltdichtungen anliegt. Jedoch ist bei einer solchen Lageranordnung nachteilig, dass der Kragen und das Lager die Schiefscheibe und die Reihe der die Kolbenköpfe an der Schiefscheibe abstützenden Kolbengleitschuhe aussen umfassen müssen, was in radialer und axialer Richtung unerwünscht grosse Bauformen und insgesamt, auch im Hinblick auf die Verschwenkbarkeit der Schiefscheibe, aufwendige Konstruktionen und aufgrund des grossen Durchmessers einen grösseren Reibungsverlust bedingt.In a machine of this type known from practice, the cylinder drum has a collar on its outer circumference, which protrudes axially over the drum end face in the direction of the swash plate up to the plane perpendicular to the drum axis and intersecting the point of application of the drum transverse force. Between the collar and the outer casing of the machine housing is the bearing supporting the cylinder drum in the form of a hydrodynamic plain bearing with cylindrical bearing surfaces. Thanks to this collar, the storage level, i. H. the plane of the bearing circle, the drum axis intersect directly in the area of the point of application of the drum lateral force, so that the support of the drum cylinder by the bearing also takes effect here, although the point of application of the drum lateral force in the plane running parallel to the swashplate through the centers of the piston heads and thus axially outside of the cylinder drum lies significantly in front of its face facing the swash plate. The advantage of this drum bearing is that the drum shear force is unable to exert a tilting moment on the cylinder drum, which could result in a disturbing tilting of the cylinder drum on the control surface of a control disk, which controls the supply and discharge of the pressure medium to the cylinders of the cylinder drum and at which End face of the cylinder drum facing away from the swash plate, forming gap seals. However, with such a bearing arrangement it is disadvantageous that the collar and the bearing must include the swash plate and the row of piston sliding shoes that support the piston heads on the swash plate, which is undesirably large in the radial and axial direction and overall, also with regard to the pivotability of the Swashplate, complex constructions and due to the large diameter a greater loss of friction.

Aus der FR-A-1 488511 ist eine Schiefscheiben-Axialkolbenmaschine bekannt, die als doppelt wirkende Anordnung mit zwei Schiefscheiben versehen ist, die sich zu beiden Seiten der Trommel gegenüberstehen. Die jeweils paarweise in entgegengesetzter Richtung an den Schiefscheiben angreifenden Kolben sind dabei jeweils in gemeinsamen Zylindern angeordnet. Somit ist die Druckmittelzufuhr in bzw. -abfuhr aus dem Zylinderraum nicht von der Stirnseite der Trommel aus möglich, sondern erfolgt über in axialer Richtung etwa in der Mitte der Zylinder mündende, dort radial verlaufende Druckmittelleitungen. Um den hierfür nötigen Raum zu schaffen, muss die Zylindertrommel einen entsprechend grösseren Durchmesser aufweisen, was zu einer unerwünscht grossen Bauform in radialer Richtung führt und damit aufgrund des grossen Durchmessers erhöhte Reibungsverluste verursacht. Die Zylindertrommel ist im übrigen durch zwei Lager jeweils etwa im Bereich ihrer Stirnseiten gelagert. Da die Trommelquerkräfte somit jeweils zwischen den beiden Lagern angreifen, werden Kippmomente an der Zylindertrommel sicher abgefangen. Jedoch verursacht das zweite Lager weitere Reibungsverluste; darüber hinaus wird die Lagerung der Zylindertrommel jedenfalls dann überbestimmt, wenn deren Lagerung am Steuerspiegel mitberücksichtigt wird.From FR-A-1 488511 a swash plate axial piston machine is known, which is provided as a double-acting arrangement with two swash plates, which face each other on both sides of the drum. The pistons engaging the swash plates in pairs in the opposite direction are each arranged in common cylinders. Thus, the pressure medium supply or discharge from the cylinder space is not possible from the front side of the drum, but takes place via pressure medium lines which open in the axial direction approximately in the middle of the cylinders and run radially there. In order to create the space required for this, the cylinder drum must have a correspondingly larger diameter, which leads to an undesirably large design in the radial direction and thus causes increased friction losses due to the large diameter. The cylinder drum is supported by two bearings each approximately in the area of their end faces. Since the drum lateral forces act between the two bearings, tilting moments on the cylinder drum are safely absorbed. However, the second bearing causes further friction losses; In addition, the storage of the cylinder drum is determined in any case if its storage on the control mirror is also taken into account.

Bei der aus der FR-A-2 359 997 bekannt gewordenen Axialkolbenmaschine besitzt die Zylindertrommel ebenfalls einen Kragen, der über die Trommelstirnseite in Richtung zur Schiefscheibe axial bis über die den Angriffspunkt der Trommelquerkraft schneidende Ebene vorsteht. Dabei ist der Kragen hier innenseitig, also im achsennahen Bereich angeordnet. Dadurch ragt der Kragen bis unmittelbar zur Schiefscheibe vor, was deren Verschwenkbarkeit erschwert oder gar unmöglich macht. Daher ist bei dieser Axialkolbenmaschine die Verstellbarkeit der Schiefscheibe auch nicht vorgesehen.In the axial piston machine which has become known from FR-A-2 359 997, the cylinder drum also has a collar which projects axially over the end face of the drum in the direction of the swash plate up to the plane intersecting the point of application of the drum transverse force. The collar is arranged on the inside here, that is to say in the region near the axis. As a result, the collar protrudes right up to the swashplate, which makes it difficult or even impossible to pivot. Therefore, the adjustability of the swash plate is not provided in this axial piston machine.

Die FR-A-1 599630 und die FR-A-2115902 beschreiben Axialkolbenmaschinen, bei denen die Zylindertrommel axial etwa mittig gelagert ist. Die radial wirkende Trommelquerkraft greift daher hier ausserhalb des Lagerbereichs an und führt somit zu einem unerwünschten Kippmoment der Zylindertrommel.FR-A-1 599630 and FR-A-2115902 describe axial piston machines in which the cylinder drum is axially mounted approximately in the middle. The radial shear force acting on the drum therefore acts outside the bearing area and thus leads to an undesired tilting moment of the cylinder drum.

Der Erfindung liegt die Aufgabe zugrunde, bei einer Axialkolbenmaschine der eingangs genannten Art das Lager der Zylindertrommel so anzuordnen und auszubilden, dass auch ohne eine äussere Umfassung der Schiefscheibe und der Kolbengleitschuhe durch Kragen und Lager eine Abstützung derZylindertrommef erhalten wird, diean derZylin-' dertrommel keine oder nur Kippmomente von so geringer Grösse entstehen lässt, dass diese Restmomente ohne Nachteil von der Steuerscheibe aufgenommen werden können.The object of the invention is to arrange and design the bearing of the cylinder drum in an axial piston machine of the type mentioned at the outset in such a way that even without an external encirclement of the swash plate and the piston sliding shoes, the cylinder drum is not supported by collars and bearings, and none on the cylinder drum or only causes tilting moments of such a small size that these residual moments can be absorbed by the control disk without disadvantage.

Diese Aufgabe wird nach der Erfindung dadurch gelöst, dass die Ebene des Lagers (d. i. die Ebene des Lagerkreises) die Trommelachse mit Abstand vom Angriffspunkt der Trommelquerkraft auf der Seite der Zylindertrommel schneidet, und dass die Wirkungsgerade der Resultierenden aller auf der Führungsbahn des Lagers senkrecht stehenden Lagerkräfte einen spitzen Winkel mit der Trommelachse einschliesst und die Trommelachse im Bereich des Angriffspunktes der Trommelquerkraft schneidet.This object is achieved according to the invention in that the plane of the bearing (ie the plane of the bearing circle) intersects the drum axis at a distance from the point of application of the drum transverse force on the side of the cylinder drum, and in that the line of action of the resultants of all of them standing vertically on the guideway of the bearing Bearing forces include an acute angle with the drum axis and intersects the drum axis in the area of the point of application of the drum lateral force.

Nach der Erfindung liegen die zur Führungsbahn senkrecht stehenden Lagerkräfte in der Mantelfläche eines Kegels, dessen Spitze als Angriffspunkt der einzelnen Lagerkräfte gedacht werden kann. Der Grundkreis des Kegels ist vom Lagerkreis des Lagers gebildet und die in der Trommelachse liegende Kegelspitze fällt mit dem Angriffspunkt der Trommelquerkraft entweder zusammen oder liegt doch so dicht neben ihm, dass der geringe Abstand zwischen der Trommelquerkraft und der resultierenden Lagerkraft keine störenden Kippmomente auf die Zylindertrommel entstehen lässt. Die Höhe des Kegels zwischen der Kegelspitze und dem Grundkreis des Kegels istgleich dem Mass, um das die Lagerebene axial vom Angriffspunkt der Trommelquerkraft weg zur Zylindertrommel hin verlagert werden kann, ohne dass sich der Angriffspunkt der resultierenden Lagerkraft auf der Trommelachse entsprechend verschiebt und vom Angriffspunkt der Trommelquerkraft entfernt. Im Ergebnis kann unter Beibehaltung der im Bereich des Angriffspunktes der Trommelquerkraft wirksam werdenden Lagerabstützung der Zylindertrommel das Lager selbst axial so weit vom Angriffspunkt der Trommelquerkraft und von der Schiefscheibe entfernt zur Zylindertrommel hin verlegt werden, dass es axial weit vor der Schiefscheibe und im Bereich der Zylindertrommel selbst liegt, und dass daher das Lager die Schiefscheibe nicht mehr radial aussen zu umfassen braucht und auch kein das Lager tragender Kragen mehr benötigt wird, weil das Lager unmittelbar an der Zylindertrommel selbst sitzen kann. Das ermöglicht geringe axiale und radiale Bauabmessungen und einen insgesamt geringeren konstruktiven und baulichen Aufwand. - Zu dem Bereich, innerhalb dem die Trommelquerkraft und die resultierende Lagerkraft axial auseinander liegen können, ist noch anzumerken, dass der Angriffspunkt der Trommelquerkraft tatsächlich immer eine geringfügige periodische Verlagerung auf der Trommelachse in Abhängigkeit vom Umlauf der Zylindertrommel zeigt, so dass er mit der Kegelspitze immer nur vorübergehend exakt zusammenfallen kann. Jedoch ist dieser Bereich, in dem derAngriffspunkt der Trommelquerkraft und die Kegelspitze auf der Trommelachse mindestens auseinander liegen können, so klein, dass hierdurch bedingte Kippmomente auf die Zylindertrommel vernachlässigt werden können. - Da die zur Trommelachse geneigte Resultierende der Lagerkraft selbstverständlich nur mit ihrer radialen Kraftkomponente der Trommelquerkraft das Gleichgewicht halten kann, muss die axiale Kraftkomponente an der Zylindertrommel selbst aufgefangen werden. Das aber ist unschwer möglich, da diese axiale Kraftkomponente bei den in der Praxis in Frage kommenden Winkeln von immer mehr als 60° zwischen der Resultierenden der Lagerkräfte und der Trommelachse nur wenige Prozent der ohnehin an der Zylindertrommel aufzunehmenden und auszugleichenden Axialkräfte beträgt, die vom Druck des Fördermittels auf die Zylindertrommel direkt ausgeübt werden.According to the invention, the bearing forces perpendicular to the guideway lie in the lateral surface of a cone, the tip of which can be thought of as the point of application of the individual bearing forces. The base circle of the cone is formed by the bearing circle of the bearing and the cone tip lying in the drum axis either coincides with the point of application of the drum transverse force or is so close to it that the small distance between the drum transverse force and the resulting bearing force does not cause any disruptive tilting moments on the cylinder drum creates. The height of the cone between the tip of the cone and the base circle of the cone is equal to the amount by which the bearing plane can be axially displaced away from the point of application of the drum transverse force towards the cylinder drum without the point of application of the resulting bearing force on the drum axis shifting accordingly and from the point of application of the Drum shear force removed. As a result, while maintaining the bearing support of the cylinder drum that becomes effective in the area of the point of application of the drum lateral force, the bearing itself can be moved axially far enough from the point of application of the drum lateral force and from the swash plate to the cylinder drum that it is axially far in front of the swash plate and in the area of the cylinder drum itself, and that therefore the bearing no longer needs to enclose the swash plate radially on the outside and also no longer a collar supporting the bearing is needed because the bearing can sit directly on the cylinder drum itself. This enables small axial and radial dimensions and overall less construction and construction effort. - Regarding the area within which the drum lateral force and the resulting bearing force can lie axially apart, it should also be noted that the point of application of the drum lateral force actually always shows a slight periodic shift on the drum axis depending on the rotation of the cylinder drum, so that it with the cone tip can only coincide exactly temporarily. However, this area, in which the point of application of the drum transverse force and the cone tip on the drum axis can be at least apart, is so small that tilting moments on the cylinder drum caused thereby can be neglected. - Since the resultant of the bearing force inclined to the drum axis can of course only keep the balance with its radial force component of the drum transverse force, the axial force component must be absorbed on the cylinder drum itself. However, this is not difficult, since this axial force component at the angles of more than 60 ° between the resultant of the bearing forces and the drum axis in practice is only a few percent of the axial forces to be absorbed and compensated for on the cylinder drum, that of the pressure of the funding can be exerted directly on the cylinder drum.

Eine bevorzugte Ausführungsform der Erfindung ist dadurch gekennzeichnet, dass die Führungsbahn von einer konischen Ringfläche gebildet ist, deren Konusspitze in der Trommeiachse auf derselben Seite des Kraftangriffspunktes der Trommelquerkraft wie die Zylindertrommel liegt und die so breit ist, dass der Angriffspunkt der Trommelquerkraft innerhalb oder zumindest dicht neben der Projektion der konischen Ringfläche in Richtung ihrer Flächennormalen auf derTrommelachse liegt. Die konische Ringfläche sollte daher mindestens so breit sein, dass ihre Projektion auf die Trommelachse jedenfalls die schon erwähnte periodische Axialverlagerung des Angriffspunktes der Trommelquerkraft auf der Trommelachse einschliesst. Dann geht jede in diesem Angriffspunkt ansetzende Lagerstützkraft immer durch die konische Ringfläche des Lagers.A preferred embodiment of the invention is characterized in that the guideway is formed by a conical ring surface, the cone tip of which lies in the drum axis on the same side of the force application point of the drum transverse force as the cylinder drum and which is so wide that the point of application of the drum transverse force is inside or at least tight next to the projection of the conical ring surface in the direction of its surface normal on the drum axis. The conical ring surface should therefore be at least so wide that its projection onto the drum axis in any case includes the aforementioned periodic axial displacement of the point of application of the drum transverse force on the drum axis. Then each bearing support force applied in this point of attack always passes through the conical ring surface of the bearing.

Im einzelnen besteht die Möglichkeit, das Lager unmittelbarzwischen der äusseren Umfangsfläche der Zylindertrommel und dem Gehäusemantel des Maschinengehäuses im Bereich der der Schiefscheibe zugewandten Stirnseite der Zylindertrommel anzuordnen. Das ergibt vorteilhaft grosse Winkel zwischen derTrommelachse einerseits und der Resultierenden der Lagerkräfte andererseits. Anstelle einer solchen Aussenlagerung der Zylindertrommel besteht aber auch die Möglichkeit einer Innenlagerung. Sie ist dadurch gekennzeichnet, dass das Maschinengehäuse einen am Maschinengehäuse festen, mit der Trommelachse koaxialen Zapfen aufweist, und dass das Lager zwischen diesem Zapfen und der Zylindertrommel angeordnet ist. Dabei kann der Zapfen die Schiefscheibe zur Zylindertrommel hin durchsetzen und hohl ausgebildet sein, so dass er eine mit der Zylindertrommel verbundene Welle aufnehmen kann. Der Zapfen kann aber auch vom anderen Ende des Maschinengehäuses her durch eine zentrale Bohrung der Zylindertrommel greifen. In allen Fällen kann das Lager als hydrodynamisch oder hydrostatisch wirkendes Gleitlager oder als Kegelrollenlager ausgebildet sein.In particular, there is the possibility of arranging the bearing directly between the outer circumferential surface of the cylinder drum and the housing jacket of the machine housing in the region of the end face of the cylinder drum facing the swash plate. This advantageously results in large angles between the drum axis on the one hand and the resultant of the bearing forces on the other. Instead of such an outer bearing of the cylinder drum, there is also the possibility of an inner bearing. It is characterized in that the machine housing has a pin which is fixed to the machine housing and is coaxial with the drum axis, and in that the bearing is arranged between this pin and the cylinder drum. The pin can pass through the swash plate towards the cylinder drum and can be hollow so that it can receive a shaft connected to the cylinder drum. The pin can also reach from the other end of the machine housing through a central bore in the cylinder drum. In all cases, the bearing can be designed as a hydrodynamically or hydrostatically acting slide bearing or as a tapered roller bearing.

Im folgenden wird die Erfindung an dem in der Zeichnung dargestellten Ausführungsbeispiel näher erläutert; es zeigen:

  • Fig. 1 eine Schiefscheiben-Axialkolbenmaschine nach der Erfindung in einem Axialschnitt, mit einer in der Teilfigur 1 a dargestellten weiteren Lagerausführung,
  • Fig. 2 eine andere Ausführungsform der erfindungsgemässen Maschine in einer der Fig. 1 entsprechenden Darstellung,
  • Fig. 3 eine weitere Ausführungsform der Erfindung.
In the following the invention is explained in more detail using the embodiment shown in the drawing; show it:
  • 1 is a swash plate axial piston machine according to the invention in an axial section, with a further bearing design shown in the partial figure 1 a,
  • 2 shows another embodiment of the machine according to the invention in a representation corresponding to FIG. 1,
  • Fig. 3 shows another embodiment of the invention.

Die in den Figuren dargestellten Axialkolbenmaschinen besitzen eine mit einer Welle 1 verbundene Zylindertrommel 2 und in den Zylindern 3 angeordnete Kolben 4. Die Kolbenköpfe 5 sind über Gleitschuhe 6 auf der Gleitfläche einer Schiefscheibe 7 abgestützt, die bezüglich ihres Neigungswinkels verstellbar im -Maschinengehäuse 8 gelagert ist. Durch die Neigung der Schiefscheibe 7 erzeugen die bei Druck des Fördermediums entstehenden Kolbenkräfte an jedem Kolben 4 eine zur Gleitebene der Schiefscheibe 7 senkrecht stehende Kraft, die mit ihrer axialen Kraftkomponente der Kolbenkraft das Gleichgewicht hält und im übrigen eine Kolbenquerkraft Pks zur Folge hat, die - summiert über alle Kolben 4- neben dem auf die Trommelachse 9 bezogenen nützlichen Drehmoment an der Zylindertrommel 2 auch eine radial wirkende Trommelquerkraft PkRes mit in der Trommelachse 9 liegendem Kraftangriffspunkt 10 zur Folge hat. Die Welle 1 ist je nach Verwendung der Maschine eine Antriebswelle im Fall einer Pumpe und eine Abtriebswelle im Fall eines Motors. Sie ist mittels eines Lagers 11 im Maschinengehäuse 8 gelagert. Ausserdem ist die Zylindertrommel 2 am Maschinengehäuse 8 in einem weiteren Lager 12 abgestützt. Die Ebene 13 dieses Lagers 12schneidet die Trommelachse 9 in einem Abstand vom Angriffspunkt 10 der Trommelquerkraft PkRes auf der Seite der Zylindertrommel 2. Die Wirkungsgerade 14 der auf der Führungsbahn 15 des Lagers 12 senkrecht stehenden resultierenden Lagerkräfte schliesst mit der Trommelachse 9 einen spitzen Winkel 26 ein und schneidet die Trommelachse 9 im Bereich des Angriffspunktes 10 der Trommelquerkraft PkRes. Der Winkel 26 ist in der Praxis grösser als etwa 60°.The axial piston machines shown in the figures have a cylinder drum 2 connected to a shaft 1 and pistons 4 arranged in the cylinders 3. The piston heads 5 are supported by sliding shoes 6 on the sliding surface of a swash plate 7, which is adjustable in the machine housing 8 with respect to its angle of inclination . Due to the inclination of the swash plate 7, the piston forces generated at the pressure of the pumped medium produce one on each piston 4 relative to the sliding plane of the swash plate 7 vertical force, which maintains the equilibrium with its axial force component of the piston force and, moreover, results in a piston shear force Pks, which - in addition to the useful torque on the cylinder drum 2 related to the drum axis 9 - also adds a radially acting drum shear force across all the pistons 4 PkRes with the force application point 10 lying in the drum axis 9. Depending on the use of the machine, shaft 1 is a drive shaft in the case of a pump and an output shaft in the case of a motor. It is mounted in the machine housing 8 by means of a bearing 11. In addition, the cylinder drum 2 is supported on the machine housing 8 in a further bearing 12. The plane 13 of this bearing 12 intersects the drum axis 9 at a distance from the point of application 10 of the drum transverse force PkRes on the side of the cylinder drum 2. The line of action 14 of the resulting bearing forces perpendicular to the guideway 15 of the bearing 12 forms an acute angle 26 with the drum axis 9 and cuts the drum axis 9 in the area of the point of application 10 of the drum lateral force PkRes. In practice, the angle 26 is greater than approximately 60 °.

Das Lager 12 kann, wie in Fig. 1 a dargestellt, ein Kugellager sein, wobei die Führungsbahn 15 zu einer linienhaften Berührung zwischen der Kugelreihe 16 einerseits und den Kugellaufbahnen 17 andererseits verengt sein kann. Zumeist aber wird die Führungsbahn 15 von einer konischen Ringfläche gebildet sein, wie es in den Fig. 1, 2 und 3 dargestellt ist. Die Konusspitze 18 dieser konischen Ringfläche liegt in der Trommelachse 9 auf derselben Seite des Kraftangriffspunktes 10 wie die Zylindertrommel 2. Die konische Ringfläche ist im übrigen so breit, dass der Angriffspunkt 10 der Trommelquerkraft PkRes innerhalb der in Fig. 1 mit X bezeichneten Projektion der konischen Ringfläche in Richtung ihrer Flächennormalen 19 auf die Trommelachse 9 liegt. Das Lager 12 kann als hydrodynamisch oder hydrostatisch wirkendes Gleitlager, wie in den Figuren jeweils in der rechten Figurenhälfte dargestellt, oder als Kegelrollenlager, wie in den Figuren links dargestellt, ausgebildet sein. In Fig. 1 ist das Lager 12 unmittelbar zwischen der äusseren Umfangsfläche 20 der Zylindertrommel 2 und dem Gehäusemantel 2 des Maschinengehäuses 8 im Bereich der der Schiefscheibe 7 zugewandten Stirnseite 22 der Zylindertrommel 2 angeordnet. Die Fig. 2 und 3 dagegen zeigen den Fall, dass das Maschinengehäuse 8 einen am Maschinengehäuse festen, zur Trommelachse 9 koaxialen Zapfen 23 aufweist, zwischen dem und der Zylindertrommel 2 das Lager 12 angeordnet ist. In Fig. 2 steht der hohl ausgebildete Zapfen 23 vom unteren Teil des Maschinengehäuses 8 durch die Schiefscheibe 7 zur Zylindertrommel 2 hin vor und nimmt die Welle 1 auf. In Fig. 3 dagegen greift der entgegengesetztzu Fig. 2 angeordnete Zapfen 23 durch eine zentrale Bohrung der Zylindertrommel 2. In allen Fällen IiegtdieZylindertrommel 2 an ihrer der Schiefscheibe 7 abgewandten Stirnseite der Steuerfläche einer die Zu-und Abfuhr des Fördermittels zu den Zylindern 3 steuernden Steuerscheibe 24 an. Die Zu- und Abfuhr des Fördermittels erfolgt an den Anschlüssen 25.The bearing 12 can, as shown in FIG. 1 a, be a ball bearing, wherein the guideway 15 can be narrowed to a linear contact between the row of balls 16 on the one hand and the ball raceways 17 on the other. But mostly the guideway 15 will be formed by a conical ring surface, as shown in FIGS. 1, 2 and 3. The conical tip 18 of this conical ring surface lies in the drum axis 9 on the same side of the force application point 10 as the cylinder drum 2. The conical ring surface is otherwise so wide that the application point 10 of the drum transverse force PkRes within the projection of the conical in FIG Ring surface lies in the direction of its surface normal 19 on the drum axis 9. The bearing 12 can be designed as a hydrodynamically or hydrostatically acting slide bearing, as shown in the figures in the right half of the figure, or as a tapered roller bearing, as shown in the figures on the left. In FIG. 1, the bearing 12 is arranged directly between the outer peripheral surface 20 of the cylinder drum 2 and the housing jacket 2 of the machine housing 8 in the region of the end face 22 of the cylinder drum 2 facing the swash plate 7. 2 and 3, on the other hand, show the case where the machine housing 8 has a pin 23, which is fixed to the machine housing and coaxial to the drum axis 9, between which and the cylinder drum 2 the bearing 12 is arranged. In Fig. 2, the hollow pin 23 protrudes from the lower part of the machine housing 8 through the swash plate 7 to the cylinder drum 2 and receives the shaft 1. In FIG. 3, on the other hand, the pin 23 arranged opposite to FIG. 2 engages through a central bore in the cylinder drum 2. In all cases, the cylinder drum 2 lies on its end face of the control surface facing away from the swash plate 7 of a control disc that controls the supply and removal of the conveying means to the cylinders 3 24 on. The supply and discharge of the funding takes place at the connections 25.

Claims (7)

1. A hydraulic swash plate axial piston machine comprising a cylinder drum (2) and pistons (4) which are arranged in the cylinders (3) of the cylinder drum (2) and whose piston heads (5) are supported against the swash plate (7) while the cylinder drum is supported axially against a control surface, wherein the piston heads, besides the useful torque related to the drum axis (9), also produce at the cylinder drum (2) a radially acting transverse drum force (PkRes) with the point (10) at which the force acts lying on the drum axis (9), the transverse force being carried by a bearing (12) which supports the cylinder drum (12) on the housing (8) of the machine in the region of the transverse drum force (PkRes), characterised in that the plane (13) of the bearing intersects the drum axis (9) at a spacing from the point (10) at which the transverse drum force (PkRes) acts, on the side of the cylinder drum (2), and that the straight line (14) at which the resultant of all bearing forces which are perpendicular to the guide track (15) of the bearing (12) acts includes an acute angle (26) with the drum axis (9) and intersects the drum axis (9) in the region of the point (10) at which the transverse drum force (PkRes) acts.
2. An axial piston machine according to claim 1 characterised in that the guide track (15) is formed by a conical annular surface in which the tip (18) of the conical configuration lies on the drum axis (9) on the same side of the point (10) at which the transverse drum force (PkRes) acts as the cylinder drum (2) and is of such a width that the point (10) at which the transverse drum force (PkRes) acts lies within or at least closely beside the projection (X) of the conical annular surface in the direction of the line (19) normal thereto, on to the drum axis (9).
3. An axial piston machine according to claim 1 or claim 2 characterised in that the bearing (12) is arranged directly between the outer circumferential surface (20) of the cylinder drum (2) and the peripheral portion (21 ) of the housing (8) of the machine in the region of the end face (22) of the cylinder drum (2), which is towards the swash plate (7).
4. An axial piston machine according to claim 1 or claim 2 characterised in that the machine housing (8) has a trunnion (23) which is fixed to the machine housing and which is coaxial with the drum axis (9) and that the bearing (12) is arranged between said trunnion (23) and the cylinder drum (2).
5. An axial piston machine according to claim 4 characterised in that the trunnion (23) passes through the swash plate (7) towards the cylinder drum (2) and is of a hollow configuration and that the trunnion (23) accommodates a shaft (1) connected to the cylinder drum (2).
6. An axial piston machine according to claim 4 characterised in that the trunnion (23) engages through a central bore in the cylinder drum (2).
7. An axial piston machine according to one of claims 2 to 6 characterised in that the bearing (12) is in the form of a plain or taper roller bearing.
EP85902965A 1984-06-26 1985-06-19 Axial-piston hydraulic pump with inclined thrust plate Expired EP0220175B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85902965T ATE35719T1 (en) 1984-06-26 1985-06-19 HYDRAULIC AXIAL PISTON MACHINE.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3423467 1984-06-26
DE3423467A DE3423467C2 (en) 1984-06-26 1984-06-26 Hydraulic swash plate axial piston machine

Publications (2)

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EP0220175A1 EP0220175A1 (en) 1987-05-06
EP0220175B1 true EP0220175B1 (en) 1988-07-13

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US (1) US4615257A (en)
EP (1) EP0220175B1 (en)
JP (1) JP2616764B2 (en)
AU (1) AU4497785A (en)
BR (1) BR8507206A (en)
CA (1) CA1242931A (en)
DD (1) DD243732A5 (en)
DE (2) DE3423467C2 (en)
ES (1) ES287634Y (en)
MX (1) MX165040B (en)
SU (1) SU1731068A3 (en)
WO (1) WO1986000377A1 (en)

Families Citing this family (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5490444A (en) * 1994-10-03 1996-02-13 Dynex/Rivett, Inc. Piston pump with improved hold-down mechanism
US5647266A (en) * 1994-10-03 1997-07-15 Dynex/Rivett, Inc. Hold-down mechanism for hydraulic pump
US5515768A (en) * 1995-02-28 1996-05-14 Caterpillar Inc. Slipper holddown device for an axial piston pump
US5862704A (en) * 1996-11-27 1999-01-26 Caterpillar Inc. Retainer mechanism for an axial piston machine
US7874914B2 (en) 1996-12-30 2011-01-25 Igt System and method for communicating game session information
US6406271B1 (en) * 1999-05-06 2002-06-18 Ingo Valentin Swashplate type axial-piston pump
DE19953766C1 (en) * 1999-11-09 2001-08-09 Danfoss As Hydraulic axial piston machine
DE10055753B4 (en) * 1999-11-30 2013-11-28 Linde Hydraulics Gmbh & Co. Kg Hydrostatic axial piston machine in swash plate design with sliding shoe joints within the bores in the cylinder block
DE10037927C2 (en) * 2000-08-03 2002-11-14 Sauer Danfoss Neumuenster Gmbh hydraulic motor
DE10055262A1 (en) * 2000-11-08 2002-05-23 Linde Ag Hydrostatic axial piston machine in inclined disc construction method
US6705203B2 (en) 2001-11-28 2004-03-16 Sauer-Danfoss Inc. Extended male slipper servo pad arrangement for positioning swashplate and method assembling same
DE10216951A1 (en) * 2002-04-17 2003-11-06 Bosch Rexroth Ag hydrotransformer
DE102005021029A1 (en) * 2005-05-06 2006-11-09 Linde Ag Swash plate type axial piston machine with cylinder block support on a trunnion
CN100485164C (en) * 2006-12-29 2009-05-06 郭有祥 Top cycle type engine
DE102007048316B4 (en) * 2007-10-09 2010-05-27 Danfoss A/S Hydraulic axial piston machine
US20090274564A1 (en) * 2008-04-30 2009-11-05 Caterpillar Inc. Floating cup pump having swashplate mounted cup elements
US20100028169A1 (en) * 2008-07-31 2010-02-04 Caterpillar Inc. Hydraulic device having an alignment component
US8333571B2 (en) * 2008-12-12 2012-12-18 Caterpillar Inc. Pump having pulsation-reducing engagement surface
KR101190076B1 (en) 2010-03-24 2012-10-12 한국기계연구원 Cylinder-Barrel Bearing for Piston Pump
US10677354B2 (en) 2010-04-28 2020-06-09 Energy Spring Ltd. Hydraulic vehicle incorporating efficient energy storage and regeneration system
US10574088B2 (en) 2010-04-28 2020-02-25 Energy Spring Ltd. Hydraulic based efficient renewable energy storage and regeneration system
US10533582B2 (en) 2010-04-28 2020-01-14 Energy Spring Ltd. Hydraulic based efficient energy storage and regeneration system
JP5519082B2 (en) * 2010-09-21 2014-06-11 ▲華▼中科技大学 Plunger water pump
NO20140581A1 (en) * 2013-05-26 2014-11-27 Subsea Hydraulic Components As Device and method of pump for dive use
CN104865060B (en) * 2015-05-21 2017-04-12 浙江大学 Multifunctional testing stand for testing oil film field parameters of slipper pair of plunger pump
MD1000Z (en) * 2015-09-30 2016-10-31 Технический университет Молдовы Precessional hydraulic motor
FR3072736B1 (en) * 2017-10-20 2022-05-06 Ifp Energies Now ROTARY BARREL PUMP WITH SEPARATE BARREL GUIDE AND CENTERING MEANS
KR102249159B1 (en) * 2019-06-14 2021-05-07 한국하이액트지능기술 주식회사 fluid pump

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3124079A (en) * 1964-03-10 Jxanjacquxs j joyer
US2847984A (en) * 1955-11-07 1958-08-19 Gen Motors Corp Hydraulic engine-starting device
US2847938A (en) * 1955-12-01 1958-08-19 John T Gondek Hydraulic pump
FR1206702A (en) * 1957-05-02 1960-02-11 New York Air Brake Co Motor driven by pressurized fluid
US3092034A (en) * 1959-02-18 1963-06-04 Kamper Motoren G M B H Axial piston engines
DE1175994B (en) * 1959-12-09 1964-08-13 Kaemper Motoren G M B H Axial piston machine
US3256782A (en) * 1963-02-19 1966-06-21 Ebert Heinrich Piston for hydraulic axial piston units with tiltable swash plate
CH417336A (en) * 1963-06-30 1966-07-15 Thoma Hans Prof Ing Dr Axial piston machine with rotating cylinder block
DE1269494B (en) * 1964-10-24 1968-05-30 Bosch Gmbh Robert Device for pressing the piston sliding shoes against the swash plate of a pressure fluid axial piston machine
FR1469527A (en) * 1965-12-03 1967-02-17 Messier Fa Hydraulic pump or motor with rotating barrel
FR1488511A (en) * 1966-07-25 1967-07-13 Boulton Aircraft Ltd Improvements to hydraulic pumps and motors
FR1599630A (en) * 1968-09-26 1970-07-15
US3861276A (en) * 1970-03-03 1975-01-21 Messier Sa Hydraulic rotary barrel pumps or motors
US3747476A (en) * 1970-03-31 1973-07-24 Delavan Manufacturing Co Balanced hydraulic device
DE2057926A1 (en) * 1970-11-25 1972-06-08 Schaeffler Ohg Industriewerk Axial piston pump
GB1593731A (en) * 1976-07-26 1981-07-22 Secretary Industry Brit Axial piston hydraulic machines

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BR8507206A (en) 1987-08-04
DE3423467C2 (en) 1986-04-24
JPS61502551A (en) 1986-11-06
MX165040B (en) 1992-10-13
ES287634U (en) 1986-05-01
DE3563772D1 (en) 1988-08-18
CA1242931A (en) 1988-10-11
AU4497785A (en) 1986-01-24
DE3423467A1 (en) 1986-01-02
JP2616764B2 (en) 1997-06-04
ES287634Y (en) 1987-01-16
EP0220175A1 (en) 1987-05-06
SU1731068A3 (en) 1992-04-30
US4615257A (en) 1986-10-07
WO1986000377A1 (en) 1986-01-16
DD243732A5 (en) 1987-03-11

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