EP2050957B1 - Axial piston machine - Google Patents
Axial piston machine Download PDFInfo
- Publication number
- EP2050957B1 EP2050957B1 EP08014003A EP08014003A EP2050957B1 EP 2050957 B1 EP2050957 B1 EP 2050957B1 EP 08014003 A EP08014003 A EP 08014003A EP 08014003 A EP08014003 A EP 08014003A EP 2050957 B1 EP2050957 B1 EP 2050957B1
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- EP
- European Patent Office
- Prior art keywords
- sliding shoe
- axial piston
- piston machine
- lever
- 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 - Fee Related
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Classifications
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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
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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
- F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
- F04B1/124—Pistons
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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
- F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
- F04B1/124—Pistons
- F04B1/126—Piston shoe retaining means
Definitions
- the invention relates to an axial piston machine in swash plate construction, with a cylinder drum rotatably mounted about a rotation axis, wherein the cylinder drum is provided with cylinder bores, in each of which a piston is mounted longitudinally displaceable, and the pistons are supported by a respective sliding shoe on a swash plate, wherein the sliding shoes by means of a rotationally synchronous with the cylinder drum rotating retainer, in particular a retaining plate, are in operative connection.
- the U.S. Patent 4,872,394 discloses an axial piston machine in oblique axis construction. According to the FIG. 2 The pistons each have a ball head, with which the pistons are articulated in corresponding ball sockets of a drive flange. A retaining ring attached to the drive flange serves to secure the ball head of the pistons in the ball sockets of the drive flange.
- the US 2003/138331 A1 discloses an axial piston machine in a swash plate-like construction.
- the pistons are not arranged rotating and mounted longitudinally displaceable in the housing.
- the pistons are connected via a transmission arm with a flywheel, which is connected to a drive shaft.
- a balance weight is provided according to the figure 49, which is fixed to the flywheel. With the balance weight, a mass balance can be achieved to avoid imbalances.
- the pistons are supported on the swashplate by means of a respective sliding shoe. Between the piston and the shoe, a sliding shoe joint is arranged.
- a tilting moment occurs on the sliding shoes due to the centrifugal forces acting on the sliding block causes a tilting of the sliding blocks of the swash plate.
- the sliding shoes are pressed in the direction of the swash plate to prevent lifting or tilting of the sliding shoes due to the Abkippmoments.
- the retaining device can in this case be designed as a force-locking retaining device, wherein a spring device is provided, which acts on the retaining device and thus the sliding shoes in the direction of the swash plate.
- a spring device which acts on the retaining device and thus the sliding shoes in the direction of the swash plate.
- the spring force of the spring device is to be interpreted to the maximum speed.
- this results in high spring forces, which cause high contact forces of the sliding shoes on the swash plate and the cylinder drum on the control surface at low speeds.
- the high contact forces lead to increased wear of the swash plate machine.
- the retaining device can furthermore be designed as a form-fitting retaining device, which is fastened to the housing in the axial direction. Due to the play existing in the form-locking connection of the retaining device with the housing, the sliding shoes can tilt due to the centrifugal force occurring during operation of the swash plate, whereby a leakage current is produced, which leads to a deteriorated efficiency of the swash plate machine.
- the present invention has for its object to provide a hydrostatic axial piston machine of the type mentioned available, which is improved in terms of efficiency.
- the sliding blocks are in operative connection with a torque generating device formed by rocker arms, by means of which a Abkippmoment counteracting counter-torque is generated on the shoes, each shoe as a two-armed lever is associated with trained rocker arm, by means of which a force acting on the shoe contact force can be generated, which is directed opposite to the centrifugal force acting on the shoe, wherein on a provided with a first lever arm portion of the rocker arm with the shoe in contact can be brought into contact surface and formed on a second lever arm of the center of mass of the rocker arm attacks.
- the idea according to the invention thus consists of generating on the sliding shoes by means of the torque generating device a counteracting torque which counteracts the tilting moment generated by the centrifugal forces and which partially or completely compensates for the tilting moment.
- the spring force and thus the contact force can be reduced in the case of a non-positive restraint device acted upon by a spring device, resulting in lower frictional forces and thus an improved efficiency of the swashplate machine.
- the wear of the swash plate machine is reduced by the reduced contact force.
- tilting of the sliding shoes is reliably avoided by the torque generating device, as a result of which a swash plate machine according to the invention has low leakage and thus high efficiency.
- the torque generating device is formed by rocker arms, wherein each sliding block is assigned a rocker arm, by means of which a contact force acting on the sliding block can be generated, which is directed counter to the centrifugal force acting on the sliding block.
- rocker arms can be generated in a simple manner acting on the sliding shoes and the centrifugal force counteracting contact force and thus on the sliding blocks a the centrifugal force caused by the tilting moment counteracting counter-torque.
- the rocker arm is in each case designed as a two-armed lever, a contact surface which can be brought into contact with the sliding shoe being formed on a region of the rocker arm provided with a first lever arm and engaging the center of gravity of the rocker arm on a second lever arm.
- the rocker arm is thus actuated by the centrifugal force, whereby the contact force is proportional to the force acting on the rocker arm centrifugal force and thus proportional to the speed of the swash plate machine.
- the rocker arm can in this case according to a preferred embodiment of the invention in the region of a Gleitschuhhalses of the shoe with the peripheral surface of the shoe in operative connection can be brought.
- rocker arm according to a further embodiment of the invention in the region of a Gleitschuhplatte of the shoe is engageable with the peripheral surface of the shoe in operative connection.
- the mass of the rocker arm and the first lever arm and the second lever arm are designed such that the counter-torque generated by the rocker arm compensates almost or completely the tilting moment acting on the sliding shoe.
- rocker arm partially wraps around the sliding block and the area of the rocker arm provided with the second lever arm at least partially fills the space between two adjacent sliding blocks, a corresponding rocker arm mass can be made available without any additional space requirement for the rocker arms.
- the rocker arms can be arranged between the retaining device and the swash plate according to a preferred embodiment of the invention.
- a bearing component in particular a cylindrical pin, is provided for supporting the rocker arm on the retaining device.
- the rocker arms can be mounted pivotably on the retaining device in a simple manner.
- the torque generating device formed from the rocker arms can be used in a swash plate machine with a non-positive restraint device, which is acted upon by means of a spring device in the direction of the swash plate.
- the torque generating device formed from the rocker arms can be used in a swash plate machine with a positive retaining device, wherein the retaining device is supported on a housing of the axial piston machine.
- FIG. 1 is a trained as a swash plate machine 1 hydrostatic axial piston machine of the prior art shown in a longitudinal section.
- the swash plate machine 1 has a cylinder drum 3 rotatably mounted about an axis of rotation 2, which is provided with a plurality of concentrically arranged cylinder bores 4, in each of which a piston 5 is mounted longitudinally displaceable.
- the cylinder drum 3 is in this case with a concentric with the axis of rotation 2 arranged drive shaft 6 in a rotationally fixed connection.
- the pistons 5 are supported on a swash plate 8 by means of a respective sliding element 7 designed as a sliding element.
- the shoe 7 is in this case connected to the piston 5 by means of a spherical Gleitschuhgelenks 9 hinged.
- the swash plate 8 can hereby as in the FIG. 1 shown formed on a housing 10 of the swash plate machine 1, wherein the swash plate machine 1 has a fixed displacement volume.
- Swash plate 8 adjustably form, whereby the swash plate machine 1 has a variable displacement volume.
- the cylinder drum 3 is supported in the axial direction on a housing-fixed control surface 11, which is formed on a disc-shaped control base 12.
- the control floor 12 is provided with kidney-shaped control slots (not shown), which form an inlet connection and an outlet connection of the swash plate machine 1.
- the sliding blocks 7 are in operative connection with a retaining device 16 in the form of a disc-shaped retaining plate 15.
- the retainer 16 is designed as a non-positive retention device.
- the retaining plate 15 is in this case mounted on a spherical bearing component 17, which is supported on the cylinder barrel 3 by means of a spring device 18 formed by a spring or several springs.
- the spring device 18 By means of the spring device 18 in this case the sliding blocks 7 are acted upon by the bearing member 17 and the retaining plate 15 in the direction of the swash plate 8.
- FIG. 2 In the FIG. 2 is a shoe 7 of the FIG. 1 shown in an enlarged view, wherein the forces occurring during operation of the swash plate machine 1 are illustrated.
- the spring force of the spring device 18 must be designed for the high centrifugal forces F f occurring at maximum speed. At lower speeds, these high and unnecessary pressing forces F A lead to increased friction losses and thus a reduced efficiency of the swashplate machine 1 and to an increased wear of the swashplate machine 1.
- FIG. 3 Here is a swash plate machine of the prior art with a positive retention device 15 in a representation according to the FIG. 2 shown.
- the disc-shaped retaining plate 15 is in this case fastened by means of a fastening device 19, for example, formed by a Seegering arranged in a groove-shaped recess 20 of the housing 10 on the housing 10 in the axial direction.
- the tilting moment of the sliding shoe 7 caused by the centrifugal force F f in turn counteracts the moment formed by the forces F A and F B. Due to the existing manufacturing tolerances and installation reasons game of fastener 19 but the slide 7 tilts from the swash plate 8, whereby a gap 21 between the Gleitschuhplatte 7a of the shoe 7 and the swash plate 8 is formed, through which a leakage current occurs in the housing interior, the results in a deteriorated efficiency of the swash plate machine.
- the sliding blocks 7 When in the FIG. 4 illustrated swash plate machine according to the invention are the sliding blocks 7 with a torque generating device 25 in operative connection, which generate a counteracting from the centrifugal force F f on the sliding shoes 7 counteracting counter-torque.
- the torque generating device 25 is arranged between the swashplate 8 and the retaining device 16 formed by the retaining plate 15 in the region of the sliding shoe plates 7a.
- the retaining device 16 according to the FIG. 4 is designed as a non-positive retaining device, which according to the FIG. 1 by means of Spring device 18 and the spherical bearing member 17 is acted upon in the direction of the swash plate 8.
- the retainer 15 according to the FIG. 4 form as a positive retention device, which according to the FIG. 3 is secured to the housing 3 in the axial direction.
- the torque generating device 25 is - as from FIG. 5 can be seen, which shows a plan view of the retaining plate 15 and the sliding shoes 7 - of rocker arms 26, wherein each shoe 7 is associated with a rocker arm 26.
- FIG. 6 is a part of the FIG. 5 shown in an enlarged view.
- the tilting lever 26 associated with a sliding shoe 7 is mounted on the outer region of the retaining plate 15 so as to be pivotable about a pivot axis 28 arranged parallel to the axis of rotation D of the retaining plate 15 by means of a bearing component 27 designed, for example, as a cylindrical pin.
- the rocker arm 26 is in this case designed as a two-armed lever, wherein a contact surface 30 is formed on a first region of the rocker arm, which is in operative connection with the peripheral surface of the shoe 7 in the region of the shoe plate 7a.
- the contact surface 30 is in this case spaced from the pivot axis 28 about a first lever arm c.
- the second region of the rocker arm 26 opposite this region with respect to the pivot axis 28 partially wraps around the sliding shoe 7 and at least partially fills the intermediate space with the adjacent sliding shoe 7.
- the center of gravity S M of the rocker arm 26 is arranged in the second region and is spaced from the pivot axis 28 by a second lever arm d.
- the second lever arm d is larger than the first lever arm c formed here.
- FIG. 7 is one of the FIG. 2 corresponding representation of the shoe 7 of a swash plate machine 1 according to the invention with the forces acting on the shoe 7 forces.
- the contact force F k generated by the rocker arm 26 and acting on the peripheral surface of the shoe 7 in the region of the shoe plate 7 a directed inward, and thus the centrifugal force F f acting on the shoe 7.
- the contact force F k acting on the circumferential surface of the sliding shoe 7 in the region of the sliding shoe plate 7 a has the distance b from the center of the sliding shoe joint 9, whereby a counter-torque is generated by the contact force F k with the distance b, which is the from the distance a and counteracts the centrifugal force F f formed Abkippmoment the shoe 7.
- the mass of the rocker arm 26 and the lever arms c, d of the rocker arm 26 are hereby preferably designed such that the Abkippmoment formed by the centrifugal force F f and the distance a of the force formed by the contact force F k and the distance b completely or almost completely is compensated, so that the sum of the moments about the midpoint of the shoe joint 9 is zero or almost zero, resulting in low forces F A and F B or these forces F A , F B disappear.
- swash plate machine 1 with a positive retention device 26 is prevented by the counterpoise generated by the rocker arms 26 tilting of the sliding shoes 7 due to the game in the fastening means of the retainer 16 in the housing 10 effectively, creating a Increase in the leakage oil is effectively avoided and the swash plate machine according to the invention has a high efficiency.
- rocker arm 26 instead of the arrangement of the rocker arm 26 between the swash plate 8 and the retaining plate 15 in the region of the Gleitschuhplatten 7 a, it is also possible to arrange the rocker arm 26 on the cylindrical drum 3 side facing the retaining plate 15. The rocker arms 26 are thus in operative connection with the contact surface 30 with the sliding shoe neck 7b of the sliding shoe 7 arranged between the sliding shoe joint 9 and the sliding shoe plate 7a.
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- Hydraulic Motors (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Description
Die Erfindung betrifft eine Axialkolbenmaschine in Schrägscheibenbauweise, mit einer um eine Rotationsachse drehbar gelagerten Zylindertrommel, wobei die Zylindertrommel mit Zylinderbohrungen versehen ist, in denen jeweils ein Kolben längsverschiebbar gelagert ist, und die Kolben mittels jeweils eines Gleitschuhs an einer Schrägscheibe abgestützt sind, wobei die Gleitschuhe mittels einer drehsynchron mit der Zylindertrommel rotierenden Rückhalteeinrichtung, insbesondere einer Rückhalteplatte, in Wirkverbindung stehen.The invention relates to an axial piston machine in swash plate construction, with a cylinder drum rotatably mounted about a rotation axis, wherein the cylinder drum is provided with cylinder bores, in each of which a piston is mounted longitudinally displaceable, and the pistons are supported by a respective sliding shoe on a swash plate, wherein the sliding shoes by means of a rotationally synchronous with the cylinder drum rotating retainer, in particular a retaining plate, are in operative connection.
Die
Die
Bei derartigen, als Schrägscheibenmaschinen ausgebildeten Axialkolbenmaschinen stützen sich die Kolben mittels jeweils eines Gleitschuhs auf der Schrägscheibe ab. Zwischen dem Kolben und dem Gleitschuh ist hierbei ein Gleitschuhgelenk angeordnet. Im Betrieb der Schrägscheibenmaschine tritt an den Gleitschuhen aufgrund der auf den Gleitschuh einwirkenden Fliehkräfte ein Abkippmoment auf, das ein Abkippen der Gleitschuhe von der Schrägscheibe bewirkt. Mittels der Rückhalteeinrichtung werden die Gleitschuhe in Richtung der Schrägscheibe angepresst, um ein Abheben bzw. Abkippen der Gleitschuhe aufgrund des Abkippmoments zu verhindern.In such axial piston machines designed as swash plate machines, the pistons are supported on the swashplate by means of a respective sliding shoe. Between the piston and the shoe, a sliding shoe joint is arranged. During operation of the swash plate machine, a tilting moment occurs on the sliding shoes due to the centrifugal forces acting on the sliding block causes a tilting of the sliding blocks of the swash plate. By means of the retaining device, the sliding shoes are pressed in the direction of the swash plate to prevent lifting or tilting of the sliding shoes due to the Abkippmoments.
Die Rückhalteeinrichtung kann hierbei als kraftschlüssige Rückhalteeinrichtung ausgebildet sind, wobei eine Federeinrichtung vorgesehen ist, die die Rückhalteeinrichtung und somit die Gleitschuhe in Richtung der Schrägscheibe beaufschlagt. Um hierbei ein Abkippen der Gleitschuhe aufgrund der im Betrieb auftretenden Fliehkräfte sicher zu vermeiden, ist die Federkraft der Federeinrichtung auf die maximale Drehzahl auszulegen. Hierdurch ergeben sich jedoch hohe Federkräfte, die im Betrieb bei niedrigeren Drehzahlen hohe Anpresskräfte der Gleitschuhe auf die Schrägscheibe sowie der Zylindertrommel auf die Steuerfläche bewirken. Hierdurch entstehen hohe Reibungskräfte, die zu einem verringerten Wirkungsgrad der Schrägscheibenmaschine führen. Zudem führen die hohen Anpresskräfte zu einem erhöhten Verschleiß der Schrägscheibenmaschine.The retaining device can in this case be designed as a force-locking retaining device, wherein a spring device is provided, which acts on the retaining device and thus the sliding shoes in the direction of the swash plate. In order to safely avoid tilting of the sliding shoes due to the centrifugal forces occurring during operation, the spring force of the spring device is to be interpreted to the maximum speed. However, this results in high spring forces, which cause high contact forces of the sliding shoes on the swash plate and the cylinder drum on the control surface at low speeds. This results in high frictional forces, which lead to a reduced efficiency of the swash plate machine. In addition, the high contact forces lead to increased wear of the swash plate machine.
Die Rückhalteeinrichtung kann weiterhin als formschlüssige Rückhalteeinrichtung ausgebildet sein, die am Gehäuse in axialer Richtung befestigt ist. Aufgrund des in der formschlüssigen Verbindung der Rückhalteeinrichtung mit dem Gehäuse vorhandenen Spiels können hierbei die Gleitschuhe aufgrund der im Betrieb auftretenden Fliehkraft von der Schrägscheibe abkippen, wodurch ein Leckagestrom entsteht, der zu einem verschlechterten Wirkungsgrad der Schrägscheibenmaschine führt.The retaining device can furthermore be designed as a form-fitting retaining device, which is fastened to the housing in the axial direction. Due to the play existing in the form-locking connection of the retaining device with the housing, the sliding shoes can tilt due to the centrifugal force occurring during operation of the swash plate, whereby a leakage current is produced, which leads to a deteriorated efficiency of the swash plate machine.
Eine gattungsgemäße, als Schrägsscheibenmaschine ausgebildete Axialkolbenmaschine ist aus der als nächstleigender Stand der Technik angesehenen
Der vorliegenden Erfindung liegt die Aufgabe zugrunde, eine hydrostatische Axialkolbenmaschine der eingangs genannten Gattung zur Verfügung zu stellen, die hinsichtlich des Wirkungsgrades verbessert ist.The present invention has for its object to provide a hydrostatic axial piston machine of the type mentioned available, which is improved in terms of efficiency.
Diese Aufgabe wird erfindungsgemäß dadurch gelöst, dass die Gleitschuhe mit einer von Kipphebeln gebildeten Momentenerzeugungseinrichtung in Wirkverbindung stehen, mittels der ein dem Abkippmoment entgegenwirkendes Gegenmoment an den Gleitschuhen erzeugbar ist, wobei jedem Gleitschuh ein als zweiarmiger Hebel ausgebildeter Kipphebel zugeordnet ist, mittels dem eine auf den Gleitschuh wirkende Kontaktkraft erzeugbar ist, die der auf den Gleitschuh einwirkenden Fliehkraft entgegengerichtet ist, wobei an einem mit einem ersten Hebelarm versehenen Bereich des Kipphebels eine mit dem Gleitschuh in Verbindung bringbare Kontaktfläche ausgebildet ist und an einem zweiten Hebelarm der Massenschwerpunkt des Kipphebels angreift. Der erfindungsgemäße Gedanke besteht somit darin, an den Gleitschuhen mittels der Momentenerzeugungseinrichtung ein dem aus den Fliehkräften erzeugten Abkippmoment entgegenwirkendes Gegenmoment zu erzeugen, das das Abkippmoment teilweise oder vollständig kompensiert. Hierdurch kann bei einer mittels einer Federeinrichtung beaufschlagten kraftschlüssigen Rückhalteeinrichtung die Federkraft und somit die Anpresskraft verringert werden, wodurch sich geringere Reibungskräfte und somit ein verbesserter Wirkungsgrad der Schrägscheibenmaschine ergibt. Zudem wird durch die verringerte Anpresskraft der Verschleiß der Schrägscheibenmaschine verringert. Bei einer formschlüssigen Rückhalteeinrichtung wird durch die Momentenerzeugungseinrichtung ein Abkippen der Gleitschuhe sicher vermieden, wodurch eine erfindungsgemäße Schrägscheibenmaschine eine geringe Leckage und somit einen hohen Wirkungsgrad aufweist. Die Momentenerzeugungseinrichtung ist von Kipphebeln gebildet, wobei jedem Gleitschuh ein Kipphebel zugeordnet ist, mittels dem eine auf den Gleitschuh wirkende Kontaktkraft erzeugbar ist, die der auf den Gleitschuh einwirkenden Fliehkraft entgegengerichtet ist. Mit Kipphebeln kann auf einfache Weise eine auf die Gleitschuhe wirkende und der Fliehkraft entgegenwirkende Kontaktkraft und somit an den Gleitschuhen ein dem aus der Fliehkraft hervorgerufenen Abkippmoment entgegenwirkendes Gegenmoment erzeugt werden. Der Kipphebel ist jeweils als zweiarmiger Hebel ausgebildet, wobei an einem mit einem ersten Hebelarm versehenen Bereich des Kipphebels eine mit dem Gleitschuh in Verbindung bringbare Kontaktfläche ausgebildet ist und an einem zweiten Hebelarm der Massenschwerpunkt des Kipphebels angreift. Der Kipphebel ist somit von der Fliehkraft betätigt, wodurch die Kontaktkraft proportional zu der an dem Kippehebel angreifenden Fliehkraft und somit proportional zur Drehzahl der Schrägscheibenmaschine ist. Mit derartigen fliehkraftbetätigten Kipphebeln kann mit geringem Bauaufwand an den Gleitschuhen ein dem Abkippmoment entgegenwirkendes Gegenmoment erzeugt werden.This object is achieved in that the sliding blocks are in operative connection with a torque generating device formed by rocker arms, by means of which a Abkippmoment counteracting counter-torque is generated on the shoes, each shoe as a two-armed lever is associated with trained rocker arm, by means of which a force acting on the shoe contact force can be generated, which is directed opposite to the centrifugal force acting on the shoe, wherein on a provided with a first lever arm portion of the rocker arm with the shoe in contact can be brought into contact surface and formed on a second lever arm of the center of mass of the rocker arm attacks. The idea according to the invention thus consists of generating on the sliding shoes by means of the torque generating device a counteracting torque which counteracts the tilting moment generated by the centrifugal forces and which partially or completely compensates for the tilting moment. As a result, the spring force and thus the contact force can be reduced in the case of a non-positive restraint device acted upon by a spring device, resulting in lower frictional forces and thus an improved efficiency of the swashplate machine. In addition, the wear of the swash plate machine is reduced by the reduced contact force. In a positive retention device, tilting of the sliding shoes is reliably avoided by the torque generating device, as a result of which a swash plate machine according to the invention has low leakage and thus high efficiency. The torque generating device is formed by rocker arms, wherein each sliding block is assigned a rocker arm, by means of which a contact force acting on the sliding block can be generated, which is directed counter to the centrifugal force acting on the sliding block. With rocker arms can be generated in a simple manner acting on the sliding shoes and the centrifugal force counteracting contact force and thus on the sliding blocks a the centrifugal force caused by the tilting moment counteracting counter-torque. The rocker arm is in each case designed as a two-armed lever, a contact surface which can be brought into contact with the sliding shoe being formed on a region of the rocker arm provided with a first lever arm and engaging the center of gravity of the rocker arm on a second lever arm. The rocker arm is thus actuated by the centrifugal force, whereby the contact force is proportional to the force acting on the rocker arm centrifugal force and thus proportional to the speed of the swash plate machine. With such centrifugally operated rocker arms, a counter-torque counteracting the tilting moment can be generated with little construction effort on the sliding shoes.
Hierbei ergeben sich besondere Vorteile, wenn der Kipphebel an der Rückhalteeinrichtung um eine parallel zur Drehachse der Rückhalteeinrichtung angeordnete Schwenkachse schwenkbar gelagert ist und mit der Umfangsfläche des Gleitschuhs in Wirkverbindung bringbar ist. Hierdurch wird mit geringem Bauaufwand erzielt, dass die auf die Gleitschuhe einwirkende Kontaktkraft der Fliehkraft entgegenwirkt.This results in particular advantages when the rocker arm on the retainer about a parallel to the axis of rotation of the retainer arranged pivot axis is pivotally mounted and can be brought into operative connection with the peripheral surface of the shoe. As a result, it is achieved with low construction costs, that counteracts the force acting on the shoes contact force of centrifugal force.
Der Kipphebel kann hierbei gemäß einer bevorzugten Ausgestaltungsform der Erfindung im Bereich eines Gleitschuhhalses des Gleitschuhs mit der Umfangsfläche des Gleitschuhs in Wirkverbindung bringbar ist.The rocker arm can in this case according to a preferred embodiment of the invention in the region of a Gleitschuhhalses of the shoe with the peripheral surface of the shoe in operative connection can be brought.
Zudem ist es möglich, wenn der Kipphebel gemäß einer weiteren Ausgestaltungsform der Erfindung im Bereich einer Gleitschuhplatte des Gleitschuhs mit der Umfangsfläche des Gleitschuhs in Wirkverbindung bringbar ist.In addition, it is possible if the rocker arm according to a further embodiment of the invention in the region of a Gleitschuhplatte of the shoe is engageable with the peripheral surface of the shoe in operative connection.
Besondere Vorteile ergeben sich, wenn der zweite Hebelarm größer als der erste Hebelarm ist, wodurch bei einer gegebenen Kipphebelmasse eine große auf den Gleitschuh wirkende Kontaktkraft erzielbar ist und somit mit einem kleinen Bauraum aufweisenden Kipphebeln ein hohes Gegenmoment erzeugbar ist.Particular advantages arise when the second lever arm is greater than the first lever arm, whereby at a given Kipphebelmasse a large acting on the shoe contact force can be achieved and thus with a small space having Kipphebeln a high counter-torque is generated.
Gemäß einer bevorzugten Weiterbildung der Erfindung sind die Masse des Kipphebels und der erste Hebelarm sowie der zweite Hebelarm derart ausgelegt, dass das von dem Kipphebel erzeugte Gegenmoment das auf den Gleitschuh einwirkende Abkippmoment nahezu oder vollständig kompensiert.According to a preferred embodiment of the invention, the mass of the rocker arm and the first lever arm and the second lever arm are designed such that the counter-torque generated by the rocker arm compensates almost or completely the tilting moment acting on the sliding shoe.
Sofern der Kipphebel den Gleitschuh teilweise umschlingt und der mit dem zweiten Hebelarm versehene Bereich des Kipphebels den Zwischenraum zweier benachbarter Gleitschuhe zumindest teilweise ausfüllt, kann ohne zusätzlichen Bauraumbedarf für die Kipphebel eine entsprechende Kipphebelmasse zur Verfügung gestellt werden.If the rocker arm partially wraps around the sliding block and the area of the rocker arm provided with the second lever arm at least partially fills the space between two adjacent sliding blocks, a corresponding rocker arm mass can be made available without any additional space requirement for the rocker arms.
Die Kipphebel können gemäß einer bevorzugten Ausführungsform der Erfindung zwischen der Rückhalteeinrichtung und der Schrägscheibe angeordnet sein.The rocker arms can be arranged between the retaining device and the swash plate according to a preferred embodiment of the invention.
Zudem ist es möglich, die Kipphebel gemäß einer weiteren Ausführungsform der Erfindung zwischen der Rückhalteeinrichtung und der Zylindertrommel anzuordnen.In addition, it is possible to arrange the rocker arms between the retaining device and the cylinder drum according to a further embodiment of the invention.
Hinsichtlich eines geringen Bauaufwands ergeben sich Vorteile, wenn zur Lagerung des Kipphebels an der Rückhalteeinrichtung ein Lagerbauteil, insbesondere ein Zylinderstift, vorgesehen ist. Mittels jeweils eines Zylinderstiftes können die Kipphebel auf einfache Weise an der Rückhalteeinrichtung schwenkbar gelagert werden.With regard to a low construction costs, there are advantages if a bearing component, in particular a cylindrical pin, is provided for supporting the rocker arm on the retaining device. By means of a respective cylinder pin, the rocker arms can be mounted pivotably on the retaining device in a simple manner.
Die aus den Kipphebeln gebildete Momentenerzeugungseinrichtung kann bei einer Schrägscheibenmaschine mit einer kraftschlüssigen Rückhalteeinrichtung verwendet werden, die mittels einer Federeinrichtung in Richtung der Schrägscheibe beaufschlagt ist.The torque generating device formed from the rocker arms can be used in a swash plate machine with a non-positive restraint device, which is acted upon by means of a spring device in the direction of the swash plate.
Zudem kann die aus den Kipphebeln gebildete Momentenerzeugungseinrichtung bei einer Schrägscheibenmaschine mit einer formschlüssigen Rückhalteeinrichtung eingesetzt werden, bei der die Rückhalteeinrichtung an einem Gehäuse der Axialkolbenmaschine abgestützt ist.In addition, the torque generating device formed from the rocker arms can be used in a swash plate machine with a positive retaining device, wherein the retaining device is supported on a housing of the axial piston machine.
Weitere Vorteile und Einzelheiten der Erfindung werden anhand der in den schematischen Figuren dargestellten Ausführungsbeispiele näher erläutert. Hierbei zeigt
- Figur 1
- eine Axialkolbenmaschine in Schrägscheibenbauweise des Standes der Technik in einem Längsschnitt,
Figur 2- eine kraftschlüssige Rückhalteeinrichtung des Standes der Technik,
Figur 3- eine formschlüssige Rückhalteeinrichtung des Standes der Technik,
Figur 4- eine erfindungsgemäße, als Schrägscheibenmaschine ausgebildete Axialkolbenmaschine in einem Längsschnitt,
Figur 5- einen Schnitt entlang der Linie A-A der
mit einer Draufsicht auf die Rückhalteeinrichtung,Figur 4 Figur 6- einen Ausschnitt der
in einer vergrößerten Darstellung,Figur 5 Figur 7- einen Ausschnitt der
in einer vergrößerten Darstellung.Figur 4
- FIG. 1
- an axial piston machine of swash plate construction of the prior art in a longitudinal section,
- FIG. 2
- a force-locking retaining device of the prior art,
- FIG. 3
- a form-locking retention device of the prior art,
- FIG. 4
- an inventive, formed as a swash plate machine axial piston machine in a longitudinal section,
- FIG. 5
- a section along the line AA the
FIG. 4 with a plan view of the retaining device, - FIG. 6
- a section of the
FIG. 5 in an enlarged view, - FIG. 7
- a section of the
FIG. 4 in an enlarged view.
In der
Die Schrägscheibenmaschine 1 weist eine um eine Rotationsachse 2 drehbar gelagerte Zylindertrommel 3 auf, die mit mehreren konzentrisch angeordneten Zylinderbohrungen 4 versehen ist, in denen jeweils ein Kolben 5 längsverschiebbar gelagert ist. Die Zylindertrommel 3 steht hierbei mit einer konzentrisch zur Rotationsachse 2 angeordneten Triebwelle 6 in drehfester Verbindung.The swash plate machine 1 has a
Die Kolben 5 stützen sich hierbei mittels jeweils eines als Gleitschuh 7 ausgebildeten Gleitelements auf einer Schrägscheibe 8 ab. Der Gleitschuh 7 ist hierbei mit dem Kolben 5 mittels eines kugelförmigen Gleitschuhgelenks 9 gelenkig verbunden. Die Schrägscheibe 8 kann hierbei wie in der
Die Zylindertrommel 3 stützt sich in axialer Richtung an einer gehäusefesten Steuerfläche 11 ab, die an einem scheibenförmigen Steuerboden 12 ausgebildet ist. Der Steuerboden 12 ist mit nicht mehr dargestellten nierenförmigen Steuerschlitzen versehen, die einen Einlassanschluss und einen Auslassanschluss der Schrägscheibenmaschine 1 bilden.The
Die Gleitschuhe 7 stehen mit einer als scheibenförmige Rückhalteplatte 15 ausgebildeten Rückhalteeinrichtung 16 in Wirkverbindung. In der in der
In der
Bei der Rotation der Zylindertrommel 3 um die Rotationsachse 2 entsteht eine am Schwerpunkt S des Gleitschuhs 7 angreifende Fliehkraft Ff , die mit dem Abstand a des Schwerpunktes S des Gleitschuhs 7 von dem Mittelpunkt des Gleitschuhgelenks 9 ein den Gleitschuh 7 von der Schrägscheibe 8 abkippendes Abkippmoment erzeugt. Das Abkippen des Gleitschuhs 7 von der Schrägscheibe 8 wird durch zwischen der Schrägscheibe 8 und dem Gleitschuh 7 sowie dem Gleitschuh 7 und der Rückhalteplatte 15 wirkende Kräfte FA und FB verhindert, die um den Durchmesser d einer kreisförmigen Gleitschuhplatte 7a, mittels der der Gleitschuh 7 an der Schrägscheibe 8 abgestützt ist, beabstandet sind und ein dem Abkippmoment entgegenwirkendes Moment erzeugen. Die anpressende Kraft FA muss hierbei von der die Rückhalteplatte 15 beaufschlagenden Federeinrichtung 18 aufgebracht werden.During rotation of the
Um ein Abkippen der Gleitschuhe 7 von der Schrägscheibe 8 sicher zu vermeiden, muss die Federkraft der Federeinrichtung 18 auf die bei maximaler Drehzahl auftretenden hohen Fliehkräfte Ff ausgelegt werden. Bei niedrigeren Drehzahlen führen diese hohen und nicht erforderlichen anpressenden Kräfte FA zu erhöhten Reibungsverlusten und somit einem verringerten Wirkungsgrad der Schrägscheibenmaschine 1 sowie zu einem erhöhten Verschleiß der Schrägscheibenmaschine 1.In order to reliably avoid tilting of the sliding
In der
Die scheibenförmige Rückhalteplatte 15 ist hierbei mittels einer beispielsweise von einem in einer nutförmigen Ausnehmung 20 des Gehäuses 10 angeordneten Seegering gebildeten Befestigungseinrichtung 19 am Gehäuse 10 in axialer Richtung befestigt.The disc-shaped
Dem von der Fliehkraft Ff bedingten Abkippmoment des Gleitschuhs 7 wirkt wiederum das aus den Kräften FA und FB gebildete Moment entgegen. Aufgrund des aus Fertigungstoleranzen und Montagegründen vorhandenen Spiels der Befestigungseinrichtung 19 kippt jedoch der Gleitschuh 7 von der Schrägscheibe 8 ab, wodurch ein Spalt 21 wischen der Gleitschuhplatte 7a des Gleitschuhs 7 und der Schrägscheibe 8 entsteht, durch den ein Leckagestrom in den Gehäuseinnenraum auftritt, der zu einem verschlechterten Wirkungsgrad der Schrägscheibenmaschine führt.The tilting moment of the sliding
Bei der in der
Es ist jedoch ebenfalls möglich, die Rückhalteeinrichtung 15 gemäß der
Die Momentenerzeugungseinrichtung 25 besteht - wie aus der
In der
Der Kipphebel 26 ist hierbei als zweiarmiger Hebel ausgebildet, wobei an einem ersten Bereich des Kipphebels eine Kontaktfläche 30 ausgebildet ist, die mit der Umfangsfläche des Gleitschuhs 7 im Bereich der Gleitschuhplatte 7a in Wirkverbindung steht. Die Kontaktfläche 30 ist hierbei von der Schwenkachse 28 um einen ersten Hebelarm c beabstandet. Der diesem Bereich bezüglich der Schwenkachse 28 gegenüberliegende zweite Bereich des Kipphebels 26 umschlingt den Gleitschuh 7 teilweise und füllt den Zwischenraum zu dem benachbarten Gleitschuh 7 zumindest teilweise aus. Durch diese Ausgestaltung des Kipphebels 26 ist der Massenschwerpunkt SM des Kipphebels 26 im zweiten Bereich angeordnet und von der Schwenkachse 28 um einen zweiten Hebelarm d beabstandet ist. Der zweite Hebelarm d ist hierbei größer als der erste Hebelarm c ausgebildet.The
Bei einer Rotation der Zylindertrommel 3 um die Drehachse 2 dreht sich die Rückhalteplatte 15 um die Drehachse D. Hierbei greift am Massenschwerpunkt SM des Kipphebels 26 eine Fliehkraft Fs an, das mit dem zweiten Hebelarm d ein Drehmoment um die Schwenkachse 28 bewirkt, das an der Kontaktfläche 30 durch eine der Fliehkraft Fs entgegengerichtete Kontaktkraft Fk abgestützt wird, die auf den Gleitschuh 7 wirkt.During a rotation of the
Durch die Wahl der Hebelarme c, d des Kipphebels 26 wird hierbei erzielt, dass bei einer gegebenen Masse des Kipphebels 26 die Kontaktkraft Fk größer als die auf den Kipphebel 26 wirkende Fliehkraft Fs ist, wodurch eine große Kontaktkraft Fk erzielbar ist.By choosing the lever arms c, d of the
In der
Wie aus der
Die Masse des Kipphebels 26 sowie die Hebelarme c, d des Kipphebels 26 sind hierbei bevorzugt derart ausgelegt, dass das von der Fliehkraft Ff und dem Abstand a gebildete Abkippmoment von dem von der Kontaktkraft Fk und dem Abstand b gebildete Gegenmoment vollständig oder nahezu vollständig kompensiert wird, so dass die Summe der Momente um den Mittelpunkt des Gleitschuhgelenks 9 null oder nahezu null ist, wodurch sich geringe Kräfte FA und FB ergeben oder diese Kräfte FA, FB verschwinden.The mass of the
Bei einer erfindungsgemäßen Schrägscheibenmaschine 1 wird somit mittels der Momentenerzeugungseinrichtung 25 das Abkippen der Gleitschuhe 7 von der Schrägscheibe 8 wirksam vermieden. Durch die von den Kipphebeln 26 erzeugte Kontaktkraft Fk und somit das auf den Gleitschuh 7 einwirkende, dem Abkippmoment entgegenwirkende Gegenmoment kann somit bei einer erfindungsgemäßen Schrägscheibenmaschine 1 mit einer kraftschlüssigen Rückhalteeinrichtung 16 die die Gleitschuhe 7 in Richtung der Schrägscheibe 8 anpressende Federkraft der auf die Rückhalteplatte 15 wirkenden Federeinrichtung 18 reduziert werden, wodurch sich geringe Reibungskräfte zwischen den Gleitschuhen 7 und der Schrägscheibe 8 ergeben und somit ein hoher Wirkungsgrad einer erfindungsgemäßen Schrägscheibenmaschine 1 erzielbar ist. Zudem wird bei einer erfindungsgemäßen Schrägscheibenmaschine 1 mit einer von den Kipphebeln 26 gebildeten Momentenerzeugungseinrichtung 25 ein geringer Verschleiß erzielt.In a swash plate machine 1 according to the invention, therefore, tilting of the sliding
Bei einer mit einer von den Kipphebeln 26 gebildeten Momentenerzeugungseinrichtung 25 versehenen Schrägscheibenmaschine 1 mit einer formschlüssigen Rückhalteeinrichtung 26 wird durch das von den Kipphebeln 26 erzeugte Gegenmoment ein Abkippen der Gleitschuhe 7 aufgrund des Spiels in der Befestigungseinrichtung der Rückhalteeinrichtung 16 im Gehäuse 10 wirksam vermieden, wodurch eine Zunahme des Lecköls wirksam vermieden wird und die erfindungsgemäße Schrägscheibenmaschine einen hohen Wirkungsgrad aufweist.In one provided with a
Darüber hinaus wird bei einer erfindungsgemäßen Schrägscheibenmaschine 1 mit der Momentenerzeugungseinrichtung 25 die fliehkraftbedingte Kontaktkraft zwischen dem Kolben 5 und der Zylinderbohrung 4 verringert, wodurch ein Festklemmen des Kolbens 5 in der Zylinderbohrung 4 wirksam vermieden werden kann.In addition, in a swash plate machine 1 according to the invention with the
Anstelle der Anordnung der Kipphebel 26 zwischen den Schrägscheibe 8 und der Rückhalteplatte 15 im Bereich der Gleitschuhplatten 7a ist es ebenfalls möglich, die Kipphebel 26 an der der Zylindertrommel 3 zugewandten Seite der Rückhalteplatte 15 anzuordnen. Die Kipphebel 26 stehen somit der Kontaktfläche 30 mit dem zwischen dem Gleitschuhgelenk 9 und der Gleitschuhplatte 7a angeordneten Gleitschuhhals 7b des Gleitschuhs 7 in Wirkverbindung.Instead of the arrangement of the
Claims (12)
- Axial piston machine of a squashplate design, having a cylinder drum which is mounted so as to rotate about a rotational axis, wherein the cylinder drum is provided with cylinder drilled holes in each of which a piston is mounted in a longitudinally displaceable fashion, and the pistons are supported on a squashplate by means of one sliding shoe each, wherein the sliding shoes are operatively connected by means of a retaining device, in particular a retaining plate, which rotates synchronously with the cylinder drum, characterized in that the sliding shoes (7) are operatively connected to a torque-generating device (25) which is formed by rocker levers (26) and by means of which a counter-torque which counteracts the tilting torque can be generated at the sliding shoes (7), wherein each sliding shoe (7) is assigned a rocker lever (26) which is embodied as a two-armed lever and by means of which a contact force (Fk) which acts on the sliding shoe (7) and which is opposed to the centrifugal force (Ff) which acts on the sliding shoe (7) can be generated, wherein a contact face (30) which can be connected to the sliding shoe (7) is formed on a region of the rocker lever (26) which is provided with a first lever arm (c), and the centre of gravity (SM) of the rocker lever (26) acts on a second lever arm (d).
- Axial piston machine according to Claim 1, characterized in that the rocker lever (26) is mounted on the retaining device (16) so as to be pivotable about a pivoting axis (28) arranged parallel to the rotational axis (D) of the retaining device (16), and said rocker lever (26) can be operatively connected to the circumferential face of the sliding shoe (7).
- Axial piston machine according to Claim 2, characterized in that the rocker lever (26) can be operatively connected to the circumferential face of the sliding shoe (7) in the region of a sliding shoe neck (7b) of the sliding shoe (7).
- Axial piston machine according to Claim 2, characterized in that the rocker lever (26) can be operatively connected to the circumferential face of the sliding shoe (7) in the region of a sliding shoe plate (7a) of the sliding shoe (7).
- Axial piston machine according to one of Claims 1 to 4, characterized in that the second lever arm (d) is larger than the first lever arm (c).
- Axial piston machine according to one of Claims 1 to 5, characterized in that the masses of the rocker lever (26), the first lever arm (c) and the second lever arm (d) are configured in such a way that the counter-torque generated by the rocker lever (26) virtually compensates, or completely compensates, the tilting torque acting on the sliding shoe (7).
- Axial piston machine according to one of Claims 1 to 6, characterized in that the rocker lever (26) is partially wrapped around the sliding shoe (7) and the region of the rocker lever (26) which is provided with the second lever arm at least partially fills the intermediate space between two adjacent sliding shoes (7).
- Axial piston machine according to one of Claims 2 to 7, characterized in that the rocker levers (26) are arranged between the retaining device (16) and the squashplate (8).
- Axial piston machine according to one of Claims 2 to 7, characterized in that the rocker levers (26) are arranged between the retaining device (16) and the cylinder drum (3).
- Axial piston machine according to one of Claims 2 to 9, characterized in that a bearing component (27), in particular a cylinder pin, is provided for mounting the rocker lever (26) on the retaining device (16).
- Axial piston machine according to one of the preceding claims, characterized in that a spring device (18) acts on the retaining device (16) in the direction of the squashplate (8).
- Axial piston machine according to one of Claims 1 to 10, characterized in that the retaining device (16) is supported on a housing (10) of the axial piston machine.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102007049393A DE102007049393A1 (en) | 2007-10-15 | 2007-10-15 | axial piston |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2050957A1 EP2050957A1 (en) | 2009-04-22 |
EP2050957B1 true EP2050957B1 (en) | 2012-06-20 |
Family
ID=39811882
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP08014003A Expired - Fee Related EP2050957B1 (en) | 2007-10-15 | 2008-08-05 | Axial piston machine |
Country Status (4)
Country | Link |
---|---|
US (1) | US8037808B2 (en) |
EP (1) | EP2050957B1 (en) |
JP (1) | JP5311383B2 (en) |
DE (1) | DE102007049393A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102012218982A1 (en) | 2012-10-18 | 2014-06-12 | Robert Bosch Gmbh | Axial piston machine for swash plate construction, has guide shoes guided in recesses by recoil plate that is engaged behind retaining unit, where retaining unit is provided with projection that is engaged behind undercut of swash plate |
Families Citing this family (10)
Publication number | Priority date | Publication date | Assignee | Title |
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SE534209C2 (en) | 2009-10-06 | 2011-05-31 | Haldex Traction Ab | Hydraulpumpaggregat |
DE102010034188A1 (en) | 2010-08-12 | 2012-02-16 | Mpp Gbr | Adjustable hydraulic axial piston engine, in particular for wind power plants (HPP) with hydrostatic main drive and method of control |
CN102926959B (en) * | 2012-11-07 | 2016-08-03 | 三一重工股份有限公司 | A kind of swash plate plunger pump or motor |
DE102013212147A1 (en) * | 2013-06-25 | 2015-01-08 | Robert Bosch Gmbh | Swash plate machine |
DE102014104952A1 (en) | 2014-04-08 | 2015-10-08 | Linde Hydraulics Gmbh & Co. Kg | Axial piston machine in bent-axis design with sliding shoes in the drive flange |
US9719499B2 (en) * | 2015-01-16 | 2017-08-01 | Hamilton Sundstrand Corporation | Slipper retainer ball for hydraulic unit |
US9863408B2 (en) * | 2015-01-16 | 2018-01-09 | Hamilton Sundstrand Corporation | Slipper retainer for hydraulic unit |
EP3374669B1 (en) * | 2015-11-13 | 2020-12-23 | BorgWarner Sweden AB | Controlling lubrication in a stand-alone rear axle drive |
CN109236597A (en) * | 2018-11-08 | 2019-01-18 | 四川航天烽火伺服控制技术有限公司 | A kind of piston shoes plunger assembly and a kind of plunger pump |
CN114046231A (en) * | 2021-11-05 | 2022-02-15 | 中国航发北京航科发动机控制系统科技有限公司 | Friction structure of sliding shoe and supporting disk |
Family Cites Families (10)
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DE1226418B (en) * | 1962-07-12 | 1966-10-06 | Unipat A G | Device for pressing the angularly movable piston sliding blocks against the swash plate or swash plate of an axial piston machine (pump or motor) |
US3807283A (en) * | 1970-05-18 | 1974-04-30 | Cessna Aircraft Co | Axial piston pump or motor |
DD107116A1 (en) * | 1973-10-01 | 1974-07-12 | Manfred Mueller | HYDROSTATIC AXIAL PISTON MACHINE |
DE3578004D1 (en) * | 1984-02-29 | 1990-07-05 | Shimadzu Corp | AXIAL PISTON PUMP OR MOTOR WITH INCLINED AXLE. |
DE3928942A1 (en) * | 1989-08-31 | 1991-03-07 | Linde Ag | AXIAL PISTON MACHINE IN WASHING PLATE DESIGN |
US5862704A (en) * | 1996-11-27 | 1999-01-26 | Caterpillar Inc. | Retainer mechanism for an axial piston machine |
US5730042A (en) * | 1996-12-04 | 1998-03-24 | Caterpillar Inc. | Retaining device for axial piston machines |
DE19706263C1 (en) * | 1997-02-18 | 1998-07-23 | Brueninghaus Hydromatik Gmbh | Axial piston machine |
US6913447B2 (en) * | 2002-01-22 | 2005-07-05 | R. Sanderson Management, Inc. | Metering pump with varying piston cylinders, and with independently adjustable piston strokes |
DE102005047981B4 (en) * | 2005-10-06 | 2015-01-29 | Linde Hydraulics Gmbh & Co. Kg | Swash plate type axial piston machine with a retaining device for the sliding shoes supported on the swashplate |
-
2007
- 2007-10-15 DE DE102007049393A patent/DE102007049393A1/en not_active Withdrawn
-
2008
- 2008-08-05 EP EP08014003A patent/EP2050957B1/en not_active Expired - Fee Related
- 2008-09-30 US US12/241,237 patent/US8037808B2/en not_active Expired - Fee Related
- 2008-10-15 JP JP2008266151A patent/JP5311383B2/en not_active Expired - Fee Related
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102012218982A1 (en) | 2012-10-18 | 2014-06-12 | Robert Bosch Gmbh | Axial piston machine for swash plate construction, has guide shoes guided in recesses by recoil plate that is engaged behind retaining unit, where retaining unit is provided with projection that is engaged behind undercut of swash plate |
Also Published As
Publication number | Publication date |
---|---|
JP5311383B2 (en) | 2013-10-09 |
US20090095149A1 (en) | 2009-04-16 |
US8037808B2 (en) | 2011-10-18 |
JP2009097512A (en) | 2009-05-07 |
DE102007049393A1 (en) | 2009-04-16 |
EP2050957A1 (en) | 2009-04-22 |
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