EP0205982B1 - Axial-piston machine with a drive plate, a cylinder barrel, and a homokinetic joint arranged there between - Google Patents

Axial-piston machine with a drive plate, a cylinder barrel, and a homokinetic joint arranged there between Download PDF

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Publication number
EP0205982B1
EP0205982B1 EP86107345A EP86107345A EP0205982B1 EP 0205982 B1 EP0205982 B1 EP 0205982B1 EP 86107345 A EP86107345 A EP 86107345A EP 86107345 A EP86107345 A EP 86107345A EP 0205982 B1 EP0205982 B1 EP 0205982B1
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EP
European Patent Office
Prior art keywords
cylinder barrel
joint
piston machine
axial piston
machine 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
EP86107345A
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German (de)
French (fr)
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EP0205982A2 (en
EP0205982A3 (en
Inventor
Ludwig Wagenseil
Reinhold Schniederjan
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Hydromatik GmbH
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Hydromatik GmbH
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Publication date
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Publication of EP0205982A2 publication Critical patent/EP0205982A2/en
Publication of EP0205982A3 publication Critical patent/EP0205982A3/en
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Publication of EP0205982B1 publication Critical patent/EP0205982B1/en
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Classifications

    • 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
    • F04B1/2092—Means for connecting rotating cylinder barrels and rotating inclined swash plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/10—Control of working-fluid admission or discharge peculiar thereto
    • F01B3/103—Control of working-fluid admission or discharge peculiar thereto for machines with rotary cylinder block
    • F01B3/106—Control of working-fluid admission or discharge peculiar thereto for machines with rotary cylinder block by changing the inclination of the swash plate

Definitions

  • the invention relates to an axial piston machine according to the preamble of claim 1.
  • the outer part is attached to the cylinder drum and the inner part is connected to the drive pulley by an auxiliary cardan joint.
  • the auxiliary cardan joint allows both an axial and a radial adjustment of the inner part, whereby constraints due to unavoidable tolerances are avoided.
  • the outside and inside curvature of the cage corresponds to the curvatures of the inner surface of the outer part and the outer surface of the inner part, so that during the operation of the axial piston machine, the transmission of slight axial forces in the region of the joint would be possible, but this is not possible with the known design, because the inner part is not axially and radially supported in a defined manner.
  • the invention has for its object to design an axial piston machine of the type described above with simple means so that axial and radial support of the cylinder drum on the drive pulley is possible while avoiding malfunctions.
  • the recess in the drive pulley is used for the axial and radial mounting of the joint.
  • the cylindrical drum-side joint part is directly supported by the spherical outer surface resting on the cylinder drum-side joint part on the spherical inner surface of the recess. Therefore, the cage can be released from the transmission of axial or radial forces.
  • the configuration according to the invention not only comprises a simple and small design, but also enables large angular differences, namely up to about 40 °, between the axis of rotation of the drive pulley and the axis of rotation of the cylinder drum.
  • the embodiment according to the invention is not only suitable for axial piston machines with a constant delivery or swallowing volume, but in particular also for axial piston machines with variable delivery or swallowing volumes.
  • Another advantage is that a joint with the features according to the invention fits for axial piston machines with different helix angles and can therefore be used both for axial piston machines with constant delivery or displacement volumes and different helix angles as well as for axial piston machines with variable delivery or absorption volumes.
  • the configuration according to the invention is also suitable with the simultaneous arrangement of an auxiliary cardan joint, as is present in the known embodiment, because the known auxiliary cardan joint with its adaptable arrangement of the drive disk-side joint part is harmless due to the direct support of the cylinder drum-side joint part on the drive flange or attachments thereof.
  • the design according to claim 2 leads on the one hand to a simpler design because the outer part is integrated into the drive pulley. It is possible both to form the spherical inner surface on the drive pulley and to insert a separate component with a spherical inner surface on or in the drive pulley. On the other hand, this configuration also leads to a reduction in the size, because there is no space for a separate component, namely a ring bearing the spherical inner surface.
  • the cage of the joint it is fundamentally not necessary for the cage of the joint to have a spherical inner and outer surface and, as it were, to be mounted between the outer and inner part in addition to its guidance, which is predetermined by the balls.
  • the articulation part on the cylinder drum side is supported directly on the drive pulley, the cage can be mounted between the outer and inner part in a manner known per se, the cage being clamped by the direct support of the articulation part on the cylinder drum side on the drive pulley are prevented.
  • the training contained in claim 6 leads to a simplification in that an internal limitation of the inner part is eliminated.
  • the joint is nevertheless stable, because the inner part is fixed on the one hand via the balls and on the other hand via the spherical outer surface on the spherical inner surface of the outer part in a predetermined position with respect to the center of the joint.
  • the end facing away from the joint is required the cylinder drum only from radially effective bearing surfaces for the cylinder drum.
  • the bearing at the end of the cylinder drum facing away from the joint is achieved in a simple manner by a convex or concave end face which is formed on a correspondingly shaped sliding surface of the housing.
  • the radially effective bearing effect is present with both a convex and a concave front or sliding surface.
  • the aforementioned sliding surface is provided on a sliding block that can be adjusted according to the desired helix angle.
  • the embodiment according to claim 9 leads to an advantageous structure of the components, both for manufacturing reasons and for reasons of assembly and disassembly. This not only results in individual components of smaller dimensions, but also the optimal materials that are functionally moved for each component can be used. Due to the plug-in connection between the pin or the inner part and the cylinder drum, the rotational driving of the cylinder drum is ensured in a simple manner.
  • the spring force causes a tight yet elastic contact of the end face of the cylinder drum facing away from the drive pulley with the sliding surface on the housing side, as a result of which an increased seal is achieved in particular if control channels for controlling the pump or motor operation are arranged in these surfaces.
  • a permanent contact of the spherical outer surface on the inner part with the spherical inner surface on the outer part is also achieved.
  • the configuration according to the invention and the further developments according to the invention are not only suitable for axial piston machines with a constant delivery or displacement volume, but are also particularly suitable for axial piston machines with a variable delivery or absorption volume, because relatively simple oblique or swivel angles are achieved with simple components, namely those up to approx. 40 °.
  • the axial piston machine consists of a two-part housing 1 with a cover 2, a drive shaft 3, on which a drive pulley 4 is formed in one piece, a cylinder drum 5 rotating with the drive pulley 4, which is connected to the drive pulley 4 by a constant velocity joint 6, a plurality of pistons 7, which are slidably mounted in axial bores 8 of the cylinder drum 5, and an adjusting device, generally designated 9, with which the helix angle a, which the axis of rotation 11 of the cylinder drum 5 encloses with the axis of rotation 12 of the drive shaft 3, can be set.
  • the drive shaft 3 is mounted in the flange part 13 of the housing 1 by means of roller bearings 14 which are set up to absorb both radial and axial forces.
  • roller bearings 14 which are set up to absorb both radial and axial forces.
  • roller bearings 14 which are set up to absorb both radial and axial forces.
  • the homokinetic joint 6 consists of an outer part 15 with a spherical, concavely curved inner surface 16 in a recess 10 (ball socket) and an inner part 17 with a spherical outer surface 18 which bears on the spherical inner surface 16.
  • the inner part 17 comprises a ring 19, in the circumferential surface of which a plurality of curved grooves 21 are arranged.
  • the grooves 21 are also associated with curved grooves 22 in the spherical inner surface 16, and in these grooves rolling elements, for. B. balls 23, of which only one is shown.
  • the inner part 17 can be pivoted in the outer part 15 about the center of the joint 24.
  • the rolling elements are assigned a cage 25 which has a spherical outer surface 26, the curvature of which corresponds to the spherical inner surface 16 of the outer part 15, and which has a spherical inner surface 27 which corresponds to the spherical outer surface 20 of the ring 19.
  • the ring 19 is non-rotatable by means of a toothed coupling 28 which is indicated. but arranged longitudinally on a pin 29.
  • the ring 19 is in its working position tion only fixed on its side facing the drive pulley 4 by a shoulder 31, which is formed by a head 32 of the pin 29. which is formed in one piece on the pin 29 or can also be fitted with a recess 33 onto a projection 34 of the pin 29, preferably in a rotationally fixed manner.
  • the pin 29 extends into the cylinder drum 5 and is received in a bore 35 with little movement play therein.
  • a tooth coupling 36 is also arranged between the pin 29 and the cylinder drum 5, which ensures an axial displacement of the pin 29 in the bore 35 when the receptacle is secured against rotation.
  • a compression spring 37 is inserted, which is supported on the end face of the pin 29 and engages on a shoulder of the cylinder drum 5 and acts axially on it in the direction of a sliding surface 38 of the cover 2.
  • the reaction force acting on the pin 29 acts on the inner part 17 in the direction of the drive pulley 4, as a result of which the spherical outer surface 18 of the inner part 17 is constantly acted against the spherical inner surface 16 of the outer part 15.
  • the sliding surface 38 is spherically and convexly curved.
  • the end face 39 of the cylinder drum 5 resting on the sliding surface 38 is concavely curved with the same curvature.
  • the end face 39 of the cylinder drum 5 lies flat against the sliding surface 38, the system being permanent and elastic due to the compression spring force.
  • the cylinder drum 5 In operation of the axial piston machine, which can work either as a pump or a motor, the cylinder drum 5 is driven by the drive pulley 4. This is made possible by three entrainment connections, namely by the rolling elements 23 guided in the grooves 21, 22 and the toothed couplings 28, 36. During the rotation of the cylinder drum 5, the pistons 7 are pushed back and forth in the bores 8, with the hydraulic medium passing through Channels 41 is sucked or ejected, which emanate from the bores 8 and open into the end face 39.
  • the channels 41 are arranged opposite suction or pressure channels, not shown, in the sliding surface 38. A detailed description of this configuration is omitted because it is generally known.
  • the roller bodies 23 and the cage 25 are released from forces acting in the direction of the drive pulley 4 on the cylinder drum 5 or on the journal 29, which are indicated by the arrow 42.
  • This is made possible by the direct support of the pin 29 on the drive pulley 4, specifically because of the contact of the spherical outer surface 18 with the spherical inner surface 16.
  • the pin 29 is supported not only axially but also radially in the outer part 15, and thereby the storage of the cylinder drum 5 at its end facing the joint 6 is also ensured.
  • the cylindrical drum 5 is axially and radially supported by the spherical shape of the end face 39 and the sliding surface 38.
  • the drive shaft 3 and the cylinder drum 5 with the piston 7 and the joint 6 represent a preassembled structural unit which is axially fixed on the one hand between a retaining ring 43 and on the other hand by the cover 2 or the sliding surface 38 in the housing 1.
  • This configuration enables not only a simple construction, but also a simple assembly or disassembly, because the assembly can be assembled or disassembled from the lid opening 44, the axial alignment being achieved by fitting the lid 2 or the component having the sliding surface 38 The unit is fixed.
  • the adjusting device 9 comprises, in a manner known per se, a sliding shoe 46 which, with a convex sliding surface 47 curved in the shape of an arc of a circle, lies against a correspondingly curved concave sliding surface 48 of the cover 2 and can be pivoted on the sliding surface 47 thereof, which is curved around the center of the joint 24.
  • the pivoting takes place in a manner known per se by means of a slide 49 which can be displaced transversely to the housing 1 in the cover 2 and which surrounds with a driver 51 in the slide shoe 46.
  • the cylinder drum 5 and the joint 6 rotate about the center of the joint 24.
  • the delivery or swallowing volume of the axial piston machine is 0.
  • the angle b which exists between the plane E1 of the drive pulley 4 and the plane E2 in which the rolling elements are arranged, is approximately half of the swivel angle a.
  • the rolling elements 23 are always on a bisector of the angle denoted by c between the axes of rotation 11, 12 of the drive shaft 4 and the cylinder drum 5, thereby ensuring the synchronism of the joint 6.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Description

Die Erfindung bezieht sich auf eine Axialkolbenmaschine nach dem Oberbegriff des Anspruchs 1.The invention relates to an axial piston machine according to the preamble of claim 1.

Eine Axialkolbenmaschine dieser Bauart ist in der DE-AS 12 20 735 beschrieben und dargestellt.An axial piston machine of this type is described and shown in DE-AS 12 20 735.

Bei der bekannten Bauart ist das Außenteil an der Zylindertrommel befestigt und das Innenteil durch ein Hilfskardangelenk mit der Triebscheibe verbunden. Das Hilfskardanrgelenk ermöglicht sowohl eine axiale als auch eine radiale Anpassung des Innenteils, wodurch Zwängungen aufgrund von nicht vermeidbaren Toleranzen vermieden werden. Die außen- und innenseitige Krümmung des Käfigs entspricht den Krümmungen der Innenfläche des Außenteils und der Außenfläche des Innenteils, so daß im Betrieb der Axialkolbenmaschine die Übertragung von geringfügigen axialen Kräften im Bereich des Gelenks möglich wäre, jedoch ist dies bei der bekannten Ausgestaltung nicht möglich, weil das Innenteil sowohl axial als auch radial nicht definiert abgestützt ist. Außerdem ist es nicht vorteilhaft, Axialkräfte mit Hilfe des Käfigs von einem Gelenkteil auf das andere Gelenkteil zu übertragen, weil bei Axialkolbenmaschinen mit veränderlichem Förder- oder Schluckvolumen hierdurch die Beweglichkeit des Käfigs gegenüber den Gelenkteilen beeinträchtigt wird. Hierbei ist nämlich zu berücksichtigen, daß der Schwenkweg des Käfigs nur etwa 50 % des Schwenkwegs des schwenkbaren Außenteils beträgt.In the known type, the outer part is attached to the cylinder drum and the inner part is connected to the drive pulley by an auxiliary cardan joint. The auxiliary cardan joint allows both an axial and a radial adjustment of the inner part, whereby constraints due to unavoidable tolerances are avoided. The outside and inside curvature of the cage corresponds to the curvatures of the inner surface of the outer part and the outer surface of the inner part, so that during the operation of the axial piston machine, the transmission of slight axial forces in the region of the joint would be possible, but this is not possible with the known design, because the inner part is not axially and radially supported in a defined manner. In addition, it is not advantageous to transfer axial forces from one joint part to the other joint part with the aid of the cage, because in the case of axial piston machines with variable delivery or displacement volumes, the mobility of the cage relative to the joint parts is thereby impaired. It must be taken into account here that the pivoting path of the cage is only about 50% of the pivoting path of the pivotable outer part.

Der Erfindung liegt die Aufgabe zugrunde, eine Axialkolbenmaschine der eingangs bezeichneten Bauart mit einfachen Mitteln so auszugestalten, daß bei Vermeidung von Funktionsstörungen eine axiale und radiale Abstützung der Zylindertrommel an der Triebscheibe möglich ist.The invention has for its object to design an axial piston machine of the type described above with simple means so that axial and radial support of the cylinder drum on the drive pulley is possible while avoiding malfunctions.

Diese Aufgabe wird durch die im Anspruch 1 enthaltenen Merkmale gelöst.This object is achieved by the features contained in claim 1.

Bei der erfindungsgemäßen Ausgestaltung wird die Ausnehmung in der Triebscheibe zur axialen und radialen Lagerung des Gelenks herangezogen. Dabei erfolgt eine direkte Abstützung des zylindertrommelseitigen Gelenkteils durch Anlage der sphärischen Außenfläche am zylindertrommelseitigen Gelenkteil an der sphärischen Innenfläche der Ausnehmung. Deshalb kann der Käfig von der Übertragung axialer bzw. radialer Kräfte freigestellt werden.In the embodiment according to the invention, the recess in the drive pulley is used for the axial and radial mounting of the joint. The cylindrical drum-side joint part is directly supported by the spherical outer surface resting on the cylinder drum-side joint part on the spherical inner surface of the recess. Therefore, the cage can be released from the transmission of axial or radial forces.

Die erfindungsgemäße Ausgestaltung umfaßt nicht nur eine einfache und kleine Bauweise, sondern ermöglicht auch große Winkelunterschiede, nämlich bis zu etwa 40°, zwischen der Drehachse der Triebscheibe und der Drehachse der Zylindertrommel. Dabei eignet sich die erfindungsgemäße Ausgestaltung nicht nur für Axialkolbenmaschinen konstanten Förder- bzw. Schluckvolumens, sondern insbesondere auch für Axialkolbenmaschinen mit veränderlichen Förder- bzw. Schluckvolumen. Ein anderer Vorteil besteht darin, daß ein Gelenk mit den erfindungsgemäßen Merkmalen für Axialkolbenmaschinen verschiedener Schrägwinkel paßt und deshalb sowohl für Axialkolbenmaschinen mit konstantem Förder- bzw. Schluckvolumen und unterschiedlichen Schrägwinkeln als auch für Axialkolbenmaschinen mit veränderlichen Förder- bzw. Schluckvolumen eingesetzt werden kann.The configuration according to the invention not only comprises a simple and small design, but also enables large angular differences, namely up to about 40 °, between the axis of rotation of the drive pulley and the axis of rotation of the cylinder drum. The embodiment according to the invention is not only suitable for axial piston machines with a constant delivery or swallowing volume, but in particular also for axial piston machines with variable delivery or swallowing volumes. Another advantage is that a joint with the features according to the invention fits for axial piston machines with different helix angles and can therefore be used both for axial piston machines with constant delivery or displacement volumes and different helix angles as well as for axial piston machines with variable delivery or absorption volumes.

In beiden Fällen ist mit einfachen Mitteln einer sichere Funktion der Axialkolbenmaschine gewährleistet.In both cases, safe operation of the axial piston machine is ensured by simple means.

Die erfindungsgemäße Ausgestaltung eignet sich auch bei gleichzeitiger Anordnung eines Hilfskardangelenks, wie es bei der bekannten Ausgestaltung vorhanden ist, weil aufgrund der direkten Abstützung des zylindertrommelseitigen Gelenkteils am Triebflansch oder Anbauteilen desselben das bekannte Hilfskardangelenk mit seiner anpaßbaren Anordnung des triebscheibenseitigen Gelenkteils unschädlich ist.The configuration according to the invention is also suitable with the simultaneous arrangement of an auxiliary cardan joint, as is present in the known embodiment, because the known auxiliary cardan joint with its adaptable arrangement of the drive disk-side joint part is harmless due to the direct support of the cylinder drum-side joint part on the drive flange or attachments thereof.

Es ist zwar aus DE-OS 26 44 033 ansich bekannt, daß dem Gelenk zugewandte Ende der Zylindertrommel sowohl axial als auch radial mittels einer Kugel abzustützen, jedoch handelt es sich bei diesem mit Universal-Kreuzgelenk bezeichneten Gelenk nicht um ein homokinetisches Gelenk, und darüberhinaus erstreckt dieses Universal-Kreuzgelenk sich in Längsrichtung über die Kugel beidseitig hinaus, so daß sich nur verhältnismäßig kleine Schrägwinkel bzw. Schwenkwinkel realisieren lassen.It is known per se from DE-OS 26 44 033 that the joint-facing end of the cylinder drum is supported both axially and radially by means of a ball, but this joint, which is designated as a universal universal joint, is not a homokinetic joint, and moreover this universal universal joint extends in the longitudinal direction beyond the ball on both sides, so that only relatively small oblique angles or swivel angles can be realized.

Die .Ausgestaltung nach Anspruch 2 führt zum einen zu einer einfacheren Ausgestaltung, weil das Außenteil in die Triebscheibe integriert ist. Dabei ist es möglich, sowohl die sphärische Innenfläche an der Triebscheibe auszubilden als auch ein separates Bauteil mit einer sphärischen Innenfläche an bzw. in die Triebscheibe einzusetzen. Andererseits führt diese Ausgestaltung auch zu einer Verringerung der Baugröße, weil der Platz für ein separates Bauteil, nämlich ein die sphärische Innenfläche tragender Ring, entfällt.The design according to claim 2 leads on the one hand to a simpler design because the outer part is integrated into the drive pulley. It is possible both to form the spherical inner surface on the drive pulley and to insert a separate component with a spherical inner surface on or in the drive pulley. On the other hand, this configuration also leads to a reduction in the size, because there is no space for a separate component, namely a ring bearing the spherical inner surface.

Es ist bei der erfindungsgemäßen Ausgestaltung grundsätzlich nicht erforderlich, daß der Käfig des Gelenks eine sphärische Innen- und Außenfläche aufweist, und sozusagen zusätzlich zu seiner durch die Kugeln vorgegebenen Führung zwischen dem Außen- und Innenteil gelagert ist. Da bei der erfindungsgemäßen Ausgestaltung das zylindertrommelseitige Gelenkteil jedoch direkt an der Triebscheibe abgestützt ist, kann der Käfig gemäß Anspruch 3 in an sich bekannter Weise zwischen dem Außen- und Innenteil gelagert sein, wobei Klemmungen des Käfigs durch die direkte Abstützung des zylindertrommelseitigen Gelenkteils an der Triebscheibe verhindert sind.In the embodiment according to the invention, it is fundamentally not necessary for the cage of the joint to have a spherical inner and outer surface and, as it were, to be mounted between the outer and inner part in addition to its guidance, which is predetermined by the balls. However, since in the embodiment according to the invention the articulation part on the cylinder drum side is supported directly on the drive pulley, the cage can be mounted between the outer and inner part in a manner known per se, the cage being clamped by the direct support of the articulation part on the cylinder drum side on the drive pulley are prevented.

Die in den Ansprüchen 4, 5 und 7 enthaltenen Merkmale sind aus herstellungstechnischen bzw. baulichen Gründen und aus Montagegründen vorteilhaft.The features contained in claims 4, 5 and 7 are advantageous for manufacturing or structural reasons and for reasons of assembly.

Die im Anspruch 6 enthaltene-Ausbildung führt insofern zu einer Vereinfachung, weil eine innere Begrenzung des Innenteils entfällt. Das Gelenk ist trotzdem stabil, weil das Innenteil einerseits über die Kugeln und andererseits über die sphärische Außenfläche an der sphärischen Innenfläche des Außenteils in einer bezüglich des Gelenkmittelpunkts vorgegebenen Stellung fixiert ist.The training contained in claim 6 leads to a simplification in that an internal limitation of the inner part is eliminated. The joint is nevertheless stable, because the inner part is fixed on the one hand via the balls and on the other hand via the spherical outer surface on the spherical inner surface of the outer part in a predetermined position with respect to the center of the joint.

Da bei der erfindungsgemäßen Ausgestaltung die axiale Lagerung der Zylindertrommel zwischen dem Gelenk und der Steuer- bzw. Gleitfläche gewährleistet ist, und die radiale Lagerung der Zylindertrommel an ihrem dem Gelenk zugewandten Ende ebenfalls durch die erfindungsgemäße Ausgestaltung gewährleistet ist, bedarf es am dem Gelenk abgewandten Ende der Zylindertrommel lediglich von radial wirksamen Lagerflächen für die Zylindertrommel. Gemäß Anspruch 8 wird die Lagerung am dem Gelenk abgewandten Ende der Zylindertrommel in einfacher Weise durch eine konvexe oder konkave Stirnfläche erreicht, die an einer entsprechend geformten Gleitfläche des Gehäuses ausgebildet ist. Der radial wirksame Lagerungseffekt ist sowohl bei einer konvex als auch konkav geformten Stirn- bzw. Gleitfläche vorhanden. Bei einer Axialkolbenpumpe mit verstellbaren Förder- bzw. Schluckvolumen ist die vorgenannte Gleitfläche an einem Gleitschuh vorhanden, der entsprechend dem gewünschten Schrägwinkel einstellbar ist.Since in the embodiment according to the invention the axial bearing of the cylinder drum between the joint and the control or sliding surface is ensured, and the radial bearing of the cylinder drum at its end facing the joint is also ensured by the embodiment according to the invention, the end facing away from the joint is required the cylinder drum only from radially effective bearing surfaces for the cylinder drum. According to claim 8, the bearing at the end of the cylinder drum facing away from the joint is achieved in a simple manner by a convex or concave end face which is formed on a correspondingly shaped sliding surface of the housing. The radially effective bearing effect is present with both a convex and a concave front or sliding surface. In the case of an axial piston pump with adjustable delivery or absorption volume, the aforementioned sliding surface is provided on a sliding block that can be adjusted according to the desired helix angle.

Die Ausgestaltung nach Anspruch 9 führt einer sowohl aus herstellungstechnischen Gründen als auch aus Montage- bzw. Demontagegründen zu einer vorteilhaften Gliederung der Bauteile. Hierdurch ergeben sich nicht nur einzelne Bauteile kleinerer Abmessungen, sondern es können auch die für jedes Bauteil funktionsbewegten optimalen Werkstoffe eingesetzt werden. Aufgrund der zwischen dem Zapfen bzw. dem Innenteil und der Zylindertrommel vorhandenen Steckverbindung ist in einfacher Weise die Drehmitnahme der Zylindertrommel gewährleistet.The embodiment according to claim 9 leads to an advantageous structure of the components, both for manufacturing reasons and for reasons of assembly and disassembly. This not only results in individual components of smaller dimensions, but also the optimal materials that are functionally moved for each component can be used. Due to the plug-in connection between the pin or the inner part and the cylinder drum, the rotational driving of the cylinder drum is ensured in a simple manner.

Die im Anspruch 10 enthaltenen Merkmale sind in mehrfacher Hinsicht vorteilhaft. Zum einen ebenfalls aus herstellungstechnischen Gründen, weil es keiner triebscheibenseitigen Fixierung der Zylindertrommel bedarf und deshalb ein beträchtlicher Herstellungsaufwand entfällt. Das gleiche gilt auch für den Zapfen bzw. das Innenteil, bei dem eine zylindertrommelseitige Fixierung entfällt.The features contained in claim 10 are advantageous in several respects. On the one hand, also for manufacturing reasons, because there is no need to fix the cylinder drum on the drive pulley side and therefore a considerable manufacturing effort is eliminated. The same also applies to the pin or the inner part, in which there is no need for a fixing on the cylinder drum side.

Zum anderen bewirkt die Federkraft eine dichte und doch elastische Anlage der der Triebscheibe abgewandten Stirnfläche der Zylindertrommel an der gehäuseseitigen Gleitfläche, wodurch insbesondere in dem Fall eine erhöhte Abdichtung erreicht wird, wenn in diesen Flächen Steuerkanäle zur Steuerung des Pumpen- bzw. Motorbetriebes angeordnet sind. Außerdem wird gleichzeitig auch eine permanente Anlage der sphärischen Außenfläche am Innenteil an der sphärischen Innenfläche am Außenteil erreicht. Diese erfindungsgemäße Weiterbildung führt im Betrieb der axialen Kolbenmaschine zu einem ruhigen Lauf. wodurch zwangsläufig eine lange Lebensdauer vorgegeben ist.On the other hand, the spring force causes a tight yet elastic contact of the end face of the cylinder drum facing away from the drive pulley with the sliding surface on the housing side, as a result of which an increased seal is achieved in particular if control channels for controlling the pump or motor operation are arranged in these surfaces. In addition, a permanent contact of the spherical outer surface on the inner part with the spherical inner surface on the outer part is also achieved. This development according to the invention leads to a smooth running in the operation of the axial piston machine. which inevitably dictates a long service life.

Die erfindungsgemäße Ausgestaltung und die erfindungsgemäßen Weiterbildungen eignen sich nicht nur für Axialkolbenmaschinen konstanten Förder- oder Schluckvolumens, sondern sie eignen sich insbesondere auch für Axialkolbenmaschinen mit veränderlichem Förder- bzw. Schluckvolumen, weil mit einfachen Bauteilen verhältnismäßig große Schräg- bzw. Schwenkwinkel erreicht werden, nämlich solche bis ca. 40°.The configuration according to the invention and the further developments according to the invention are not only suitable for axial piston machines with a constant delivery or displacement volume, but are also particularly suitable for axial piston machines with a variable delivery or absorption volume, because relatively simple oblique or swivel angles are achieved with simple components, namely those up to approx. 40 °.

Nachfolgend wird ein bevorzugtes Ausführungsbeispiel der Erfindung anhand einer vereinfachten Zeichnung näher beschrieben. Es zeigt :

  • Fig. 1 eine erfindungsgemäß ausgestaltete Axialkolbenmaschine mit einem homokinetischen Gelenk zwischen der Triebscheibe und der Zylindertrommel im axialen Teilschnitt ;
  • Fig. 2 eine vergrößerte Darstellung des homokinetischen Gelenks und einem Teil der Zylindertrommel.
A preferred embodiment of the invention is described in more detail below with the aid of a simplified drawing. It shows :
  • 1 shows an axial piston machine designed according to the invention with a homokinetic joint between the drive pulley and the cylinder drum in partial axial section;
  • Fig. 2 is an enlarged view of the constant velocity joint and part of the cylinder drum.

Die Axialkolbenmaschine besteht aus einem zweiteiligen Gehäuse 1 mit einem Deckel 2, einer Triebwelle 3, an der einstückig eine Triebscheibe 4 ausgebildet ist, einer mit der Triebscheibe 4 umlaufenden Zylindertrommel 5, die durch ein homokinetisches Gelenk 6 mit der Triebscheibe 4 verbunden ist, einer Mehrzahl von Kolben 7, die in axialen Bohrungen 8 der Zylindertrommel 5 verschiebbar gelagert sind, und einer allgemein mit 9 bezeichneten Verstellvorrichtung, mit der der Schrägwinkel a, den die Drehachse 11 der Zylindertrommel 5 mit der Drehachse 12 der Triebwelle 3 einschließen, einzustellen ist.The axial piston machine consists of a two-part housing 1 with a cover 2, a drive shaft 3, on which a drive pulley 4 is formed in one piece, a cylinder drum 5 rotating with the drive pulley 4, which is connected to the drive pulley 4 by a constant velocity joint 6, a plurality of pistons 7, which are slidably mounted in axial bores 8 of the cylinder drum 5, and an adjusting device, generally designated 9, with which the helix angle a, which the axis of rotation 11 of the cylinder drum 5 encloses with the axis of rotation 12 of the drive shaft 3, can be set.

Die Triebwelle 3 ist im Flanschteil 13 des Gehäuses 1 mittels Wälzlager 14 gelagert, die zur Aufnahme sowohl radialer als auch axialer Kräfte eingerichtet sind. Hierzu dienen z. B. zwei spiegelbildlich zueinander angeordnete Kegelrollenlager.The drive shaft 3 is mounted in the flange part 13 of the housing 1 by means of roller bearings 14 which are set up to absorb both radial and axial forces. For this purpose, e.g. B. two mirrored tapered roller bearings.

Das homokinetische Gelenk 6 besteht aus einem Außenteil 15 mit einer sphärischen, konkav gekrümmten Innenfläche 16 in einer Ausnehmung 10 (Kugelpfanne) und einem Innenteil 17 mit einer sphärischen Außenfläche 18, die an der sphärischen Innenfläche 16 anliegt. Das Innenteil 17 umfaßt einen Ring 19, in dessen Umfangsfläche eine Mehrzahl gekrümmter Nuten 21 angeordnet sind. Den Nuten 21 sind ebenfalls gekrümmte Nuten 22 in der sphärischen Innenfläche 16 zugeordnet, und in diesen Nuten sind Wälzkörper, z. B. Kugeln 23, aufgenommen, von denen nur eine dargestellt ist. Das Innenteil 17 ist im Außenteil 15 um den Gelenkmittelpunkt 24 schwenkbar. wobei das Innenteil 17 sowohl durch die Wälzkörper als auch durch die Anlage der sphärischen Außenfläche 18 an der sphärischen Innenfläche 16 geführt ist. Den Wälzkörpern ist ein Käfig 25 zugeordnet, der eine sphärische Außenfläche 26 aufweist, deren Krümmung der sphärischen Innenfläche 16 des Außenteils 15 entspricht, und der eine sphärische Innenfläche 27 aufweist, die der sphärischen Außenfläche 20 des Rings 19 entspricht.The homokinetic joint 6 consists of an outer part 15 with a spherical, concavely curved inner surface 16 in a recess 10 (ball socket) and an inner part 17 with a spherical outer surface 18 which bears on the spherical inner surface 16. The inner part 17 comprises a ring 19, in the circumferential surface of which a plurality of curved grooves 21 are arranged. The grooves 21 are also associated with curved grooves 22 in the spherical inner surface 16, and in these grooves rolling elements, for. B. balls 23, of which only one is shown. The inner part 17 can be pivoted in the outer part 15 about the center of the joint 24. wherein the inner part 17 is guided both by the rolling elements and by the contact of the spherical outer surface 18 on the spherical inner surface 16. The rolling elements are assigned a cage 25 which has a spherical outer surface 26, the curvature of which corresponds to the spherical inner surface 16 of the outer part 15, and which has a spherical inner surface 27 which corresponds to the spherical outer surface 20 of the ring 19.

Der Ring 19 ist durch eine andeutungsweise dargestellte Zahnkupplung 28 unverdrehbar. jedoch längs verschiebbar auf einem Zapfen 29 angeordnet. Der Ring 19 ist in seiner Arbeitsposition lediglich auf seiner der Triebscheibe 4 zugewandten Seite fixiert und zwar durch eine Schulter 31, die durch einen Kopf 32 des Zapfens 29 gebildet ist. der einstückig an den Zapfen 29 angeformt oder auch mit einer Ausnehmung 33 auf einen Ansatz 34 des Zapfens 29 vorzugsweise drehfest aufgesteckt sein kann.The ring 19 is non-rotatable by means of a toothed coupling 28 which is indicated. but arranged longitudinally on a pin 29. The ring 19 is in its working position tion only fixed on its side facing the drive pulley 4 by a shoulder 31, which is formed by a head 32 of the pin 29. which is formed in one piece on the pin 29 or can also be fitted with a recess 33 onto a projection 34 of the pin 29, preferably in a rotationally fixed manner.

Der Zapfen 29 erstreckt sich bis in die Zylindertrommel 5 hinein und ist in einer Bohrung 35 mit geringem Bewegungsspiel darin aufgenommen. Zwischen dem Zapfen 29 und der Zylindertrommel 5 ist ebenfalls eine Zahnkupplung 36 angeordnet, die bei drehsicherer Aufnahme eine axiale Verschiebung des Zapfens 29 in der Bohrung 35 gewährleistet. Am Grund der Bohrung 35 ist eine Druckfeder 37 eingesetzt, die sich an der Stirnseite des Zapfens 29 abstützt und an einer Schulter der Zylindertrommel 5 angreift und diese axial in Richtung auf eine Gleitfläche 38 des Deckels 2 beaufschlagt. Die am Zapfen 29 wirksame Reaktionskraft beaufschlagt das Innenteil 17 in Richtung auf die Triebscheibe 4, wodurch die sphärische Außenfläche 18 des Innenteils 17 ständig gegen die sphärische Innenfläche 16 des Außenteils 15 beaufschlagt ist.The pin 29 extends into the cylinder drum 5 and is received in a bore 35 with little movement play therein. A tooth coupling 36 is also arranged between the pin 29 and the cylinder drum 5, which ensures an axial displacement of the pin 29 in the bore 35 when the receptacle is secured against rotation. At the bottom of the bore 35, a compression spring 37 is inserted, which is supported on the end face of the pin 29 and engages on a shoulder of the cylinder drum 5 and acts axially on it in the direction of a sliding surface 38 of the cover 2. The reaction force acting on the pin 29 acts on the inner part 17 in the direction of the drive pulley 4, as a result of which the spherical outer surface 18 of the inner part 17 is constantly acted against the spherical inner surface 16 of the outer part 15.

Die Gleitfläche 38 ist sphärisch und konvex gekrümmt. Die an der Gleitfläche 38 anliegende Stirnfläche 39 der Zylindertrommel 5 ist mit gleicher Krümmung konkav gekrümmt. Infolgedessen liegt die Zylindertrommel 5 mit ihrer Stirnfläche 39 flächig an der Gleitfläche 38 an, wobei die Anlage aufgrund der Druckfederkraft permanent und elastisch ist.The sliding surface 38 is spherically and convexly curved. The end face 39 of the cylinder drum 5 resting on the sliding surface 38 is concavely curved with the same curvature. As a result, the end face 39 of the cylinder drum 5 lies flat against the sliding surface 38, the system being permanent and elastic due to the compression spring force.

Im Betrieb der Axialkolbenmaschine, die wahlweise als Pumpe oder Motor zu arbeiten vermag, wird die Zylindertrommel 5 durch die Triebscheibe 4 angetrieben. Dies wird durch drei Mitnahmeverbindungen ermöglicht, nämlich durch die in den Nuten 21, 22 geführten Wälzkörper 23 und die Zahnkupplungen 28, 36. Während der Drehung der Zylindertrommel 5 werden die Kolben 7 in den Bohrungen 8 hin und her geschoben, wobei das hydraulische Medium durch Kanäle 41 angesaugt bzw. ausgestoßen wird, die von den Bohrungen 8 ausgehen und in der Stirnfläche 39 münden. Den Kanälen 41 sind gegenüberliegend in der Gleitfläche 38 nicht dargestellte Saug- bzw. Druckanäle angeordnet. Auf eine Detailbeschreibung dieser Ausgestaltung wird verzichtet, weil sie allgemein bekannt ist.In operation of the axial piston machine, which can work either as a pump or a motor, the cylinder drum 5 is driven by the drive pulley 4. This is made possible by three entrainment connections, namely by the rolling elements 23 guided in the grooves 21, 22 and the toothed couplings 28, 36. During the rotation of the cylinder drum 5, the pistons 7 are pushed back and forth in the bores 8, with the hydraulic medium passing through Channels 41 is sucked or ejected, which emanate from the bores 8 and open into the end face 39. The channels 41 are arranged opposite suction or pressure channels, not shown, in the sliding surface 38. A detailed description of this configuration is omitted because it is generally known.

Beim Drehen der Zylindertrommel 5 führen die Kolben 7 Pendelbewegungen aus. Dies wird durch schwenkbare in der Triebscheibe 4 gelagerte kugelförmige Kolbenköpfe 30 ermöglicht, die durch im Querschnitt verjüngte Schäfte mit den Kolben 7 verbunden sind.When the cylinder drum 5 is rotated, the pistons 7 perform oscillating movements. This is made possible by pivotable spherical piston heads 30 which are mounted in the drive disk 4 and which are connected to the pistons 7 by shafts which have a tapered cross section.

Im Betrieb der Axialkolbenmaschine sind die Wälzkörper 23 und der Käfig 25 von in Richtung auf die Triebscheibe 4 an der Zylindertrommel 5 bzw. am Zapfen 29 wirksamen Kräften freigestellt, die durch den Pfeil 42 verdeutlicht sind. Dies wird durch die unmittelbare Abstützung des Zapfens 29 an der Triebscheibe 4 ermöglicht und zwar aufgrund der Anlage der sphärischen Außenfläche 18 an der sphärischen Innenfläche 16. Aufgrund deren sphärischen Form ist der Zapfen 29 nicht nur axial sondern auch radial im Außenteil 15 abgestützt, und hierdurch ist auch die Lagerung der Zylindertrommel 5 an ihrem dem Gelenk 6 zugewandten Ende gewährleistet. An dem Gelenk 6 abgewandten Ende ist die Zylindertrommel 5 durch die sphärische Form der Stirnfläche 39 und der Gleitfläche 38 axial und radial gestützt.In the operation of the axial piston machine, the roller bodies 23 and the cage 25 are released from forces acting in the direction of the drive pulley 4 on the cylinder drum 5 or on the journal 29, which are indicated by the arrow 42. This is made possible by the direct support of the pin 29 on the drive pulley 4, specifically because of the contact of the spherical outer surface 18 with the spherical inner surface 16. Because of its spherical shape, the pin 29 is supported not only axially but also radially in the outer part 15, and thereby the storage of the cylinder drum 5 at its end facing the joint 6 is also ensured. At the end facing away from the joint 6, the cylindrical drum 5 is axially and radially supported by the spherical shape of the end face 39 and the sliding surface 38.

Die Triebwelle 3 und die Zylindertrommel 5 mit den Kolben 7 und dem Gelenk 6 stellen eine vormontierbare Baueinheit dar, die einerseits zwischen einem Sicherungsring 43 und andererseits durch den Deckel 2 bzw. die Gleitfläche 38 im Gehäuse 1 axial fixiert ist. Diese Ausgestaltung ermöglicht nicht nur eine einfache Bauweise, sondern auch eine einfache Montage bzw. Demontage, weil die Baueinheit von der Deckelöffnung 44 her montiert bzw. demontiert werden kann, wobei durch das Aufsetzen des Deckels 2 bzw. des die Gleitfläche 38 aufweisenden Bauteils die axialie Fixierung der Baueinheit erfolgt.The drive shaft 3 and the cylinder drum 5 with the piston 7 and the joint 6 represent a preassembled structural unit which is axially fixed on the one hand between a retaining ring 43 and on the other hand by the cover 2 or the sliding surface 38 in the housing 1. This configuration enables not only a simple construction, but also a simple assembly or disassembly, because the assembly can be assembled or disassembled from the lid opening 44, the axial alignment being achieved by fitting the lid 2 or the component having the sliding surface 38 The unit is fixed.

Die Verstellvorrichtung 9 umfaßt in an sich bekannter Weise einen Gleitschuh 46, der mit einer kreisbogenförmig gekrümmten konvexen Gleitfläche 47 an einer entsprechend gekrümmten konkaven Gleitfläche 48 des Deckels 2 anliegt und an dessen Gleitfläche 47, die um den Gelenkmittelpunkt 24 gekrümmt ist, verschwenkbar ist. Das Verschwenken erfolgt in an sich bekannter Weise durch einen im Deckel 2 quer zum Gehäuse 1 verschiebbaren Schieber 49, der mit einem Mitnehmer 51 in den Gleitschuh 46 einfaßt. Während des Verschwenkens drehen sich die Zylindertrommel 5 und das Gelenk 6 um den Gelenkmittelpunkt 24. In der mit 52 bezeichneten Position des Mitnehmers 51 ist der Förder- bzw. Schluckvolumen der Axialkolbenmaschine 0.The adjusting device 9 comprises, in a manner known per se, a sliding shoe 46 which, with a convex sliding surface 47 curved in the shape of an arc of a circle, lies against a correspondingly curved concave sliding surface 48 of the cover 2 and can be pivoted on the sliding surface 47 thereof, which is curved around the center of the joint 24. The pivoting takes place in a manner known per se by means of a slide 49 which can be displaced transversely to the housing 1 in the cover 2 and which surrounds with a driver 51 in the slide shoe 46. During the pivoting, the cylinder drum 5 and the joint 6 rotate about the center of the joint 24. In the position of the driver 51, designated 52, the delivery or swallowing volume of the axial piston machine is 0.

Der Winkel b, der jeweils zwischen der Ebene E1 der Triebscheibe 4 und der Ebene E2, in der die Wälzkörper angeordnet sind, besteht, beträgt etwa die Hälfte des Schwenkwinkels a. Infolgedessen befinden sich die Wälzkörper 23 immer auf einer Winkelhalbierenden des mit c bezeichneten Winkels zwischen den Drehachsen 11, 12 der Triebwelle 4 und der-Zylindertrommel 5, wodurch der Gleichlauf des Gelenks 6 gewährleistet ist.The angle b, which exists between the plane E1 of the drive pulley 4 and the plane E2 in which the rolling elements are arranged, is approximately half of the swivel angle a. As a result, the rolling elements 23 are always on a bisector of the angle denoted by c between the axes of rotation 11, 12 of the drive shaft 4 and the cylinder drum 5, thereby ensuring the synchronism of the joint 6.

Claims (11)

1. An axial piston machine of the bent axis type having a drive disc (4) and a cylinder barrel (5), wherein a plurality of pistons (7) are accommodated axially displaceably in piston bores (8) in the cylinder barrel (5) with their shafts pivotably mounted on the drive disc (4), and the drive disc (4) and the cylinder barrel (5) are connected to one another by a homokinetic joint (6) which comprises two joint parts which can be pivoted relative to one another, namely an inner part (17) and an outer part (15) and a plurality of rolling elements (23) arranged between them in a cage (25), and projects into a recess in the drive disc (4), characterised in that the recess (10) has a spherical inner surface (16) with a centre of curvature lying in the centre point (24) of the joint against which the joint part (17) on the cylinder barrel side, which has a spherical outer surface (18) of the same curvature, whose centre of curvature also lies in the centre of the joint (24), abuts with axial support of the cylinder barrel (5).
2. An axial piston machine according to claim 1, characterised in that the outer part (15) of the joint (6) is formed by or is a part of the drive disc (4), and that the inner part (17) of the joint (6) is formed by or is a part of the cylinder barrel (5).
3. An axial piston machine according to claim 1 or claim 2, characterised in that the cage (25) is curved spherically, that the external curvature of the cage (25) corresponds to the curvature of the spherical inner surface (16) of the recess (10) and the internal curvature of the cage (25) corresponds to the curvature of the one outer surface (20) of the inner part (17), and that the cage (25) is supported on the spherical inner surface (16) of the recess (10) and on the spherical outer surface (20) of the inner part (17).
4. An axial piston machine according to any one of claims 1 to 3, characterised in that in the inner part (17) comprises a ring (19) which is secured against rotation (splined connection 28) on a pin (29) of the cylinder barrel (5).
5. An axial piston machine according to claim 4, characterised in that the spherical outer surface (18) of the inner part (17) is formed on the ring (19), on the pin (29) or on a head mounted on the end of the pin (29).
6. An axial piston machine according to claim 4 or claim 5, characterised in that the ring (19) is arranged so as to be longitudinally displaceable on the pin (29) and its displaceability is axially limited only on its side facing away from the cylinder barrel (5) by a shoulder (31).
7. An axial piston machine according to claim 6, characterised in that the shoulder (31) is formed by a head (32) formed integrally with or mounted on the pin.
8. An axial piston machine according to any one of claims 1 to 7, characterised in that the face (39) of the cylinder barrel (5) facing away from the joint (6) is convex or concave, preferably spherically, and is supported against a correspondingly formed sliding surface (38) of he housing (1) or of an extension part of the latter.
9. An axial piston machine according to any one of claims 1 to 8, characterised in that the inner part (17) or the pin (29) is a separate unit which can be connected to the cylinder barrel (5) by a plug-in connection, preferably in the form of a splined connection (36).
10. An axial piston machine according to claim 8, characterised in that the inner part (17) or the pin (29) is mounted to be longitudinally displaceable, preferably in a bore (35) of the cylinder barrel (5), and that the cylinder barrel (5) is urged against the sliding surface (38) by a pressure spring (37) acting between it and the pin (29).
11. An axial piston machine according to any one of claims 1 to 10, characterised in that in order to alter the displacement (pump) or swept volume (motor) the cylinder barrel (5) can be tilted about the centre (24) of the joint by an adjusting device (9) and can be set in the respective tilt position.
EP86107345A 1985-06-25 1986-05-30 Axial-piston machine with a drive plate, a cylinder barrel, and a homokinetic joint arranged there between Expired EP0205982B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3522716 1985-06-25
DE19853522716 DE3522716A1 (en) 1985-06-25 1985-06-25 AXIAL PISTON MACHINE WITH A DRIVE DISC, A CYLINDRUM DRUM AND AN INTERMEDIATE HOMOKINETIC JOINT

Publications (3)

Publication Number Publication Date
EP0205982A2 EP0205982A2 (en) 1986-12-30
EP0205982A3 EP0205982A3 (en) 1988-01-13
EP0205982B1 true EP0205982B1 (en) 1988-12-21

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP86107345A Expired EP0205982B1 (en) 1985-06-25 1986-05-30 Axial-piston machine with a drive plate, a cylinder barrel, and a homokinetic joint arranged there between

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EP (1) EP0205982B1 (en)
DE (2) DE3522716A1 (en)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE465281B (en) * 1987-09-18 1991-08-19 Volvo Hydraulik Ab EMPLOYEE DEVICE FOR CYLINDER DRUM AT AN AXIAL PISTON VARIABLE WITH VARIABLE DEPLACEMENT
DE3739927A1 (en) * 1987-11-25 1989-06-08 Man Nutzfahrzeuge Gmbh Constant-velocity joint
US5033358A (en) * 1988-01-04 1991-07-23 Hans Molly Axial piston type motor
DE3800031A1 (en) * 1988-01-04 1989-07-20 Molly Hans Dipl Ing Dr Ing E H Axial piston machine developing torque on the cam plate
DE19829952A1 (en) * 1998-07-04 2000-01-05 Viktor Krenik High pressure oil pump for hydraulic transmission
DE102014104953A1 (en) * 2014-04-08 2015-10-08 Linde Hydraulics Gmbh & Co. Kg Hydrostatic axial piston machine in bent-axis design with a follower joint for driving the cylinder drum

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2146133A (en) * 1936-06-01 1939-02-07 Waterbury Tool Co Power transmission
DE1220735B (en) * 1958-11-21 1966-07-07 Dowty Hydraulic Units Ltd Articulated connection between the rotating cylinder drum and the drive flange of an axial piston machine that rotates at an angle to it
US4129063A (en) * 1975-10-01 1978-12-12 Ifield Engineering Pty. Limited Bent axis pumps and motors

Also Published As

Publication number Publication date
DE3522716A1 (en) 1987-01-08
EP0205982A2 (en) 1986-12-30
DE3661489D1 (en) 1989-01-26
DE3522716C2 (en) 1989-01-26
EP0205982A3 (en) 1988-01-13

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