EP1573200B1 - Axial piston engine - Google Patents
Axial piston engine Download PDFInfo
- Publication number
- EP1573200B1 EP1573200B1 EP03782132A EP03782132A EP1573200B1 EP 1573200 B1 EP1573200 B1 EP 1573200B1 EP 03782132 A EP03782132 A EP 03782132A EP 03782132 A EP03782132 A EP 03782132A EP 1573200 B1 EP1573200 B1 EP 1573200B1
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- EP
- European Patent Office
- Prior art keywords
- axial
- cylinder
- accordance
- piston machine
- piston
- 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 - Lifetime
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- 230000033001 locomotion Effects 0.000 claims description 13
- 230000002093 peripheral effect Effects 0.000 claims description 8
- 210000003734 kidney Anatomy 0.000 claims 1
- 238000010276 construction Methods 0.000 description 4
- 230000015572 biosynthetic process Effects 0.000 description 2
- 238000002788 crimping Methods 0.000 description 2
- 238000007598 dipping method Methods 0.000 description 2
- 230000004323 axial length Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 238000005553 drilling Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000036316 preload Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
Images
Classifications
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- 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
- F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F01B3/0035—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons
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- 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
- F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F01B3/0035—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons
- F01B3/0038—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons inclined to main shaft axis
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/2014—Details or component parts
- F04B1/2035—Cylinder barrels
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/22—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 having two or more sets of cylinders or 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
- F04B1/20—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
- F04B1/22—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 having two or more sets of cylinders or pistons
- F04B1/24—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 having two or more sets of cylinders or pistons inclined to the main shaft axis
Definitions
- the invention relates to an axial piston machine according to the preamble of patent claim 1.
- Such, for example, from US 2,968,286 known axial piston machine has a plurality of approximately axially arranged pistons, which are guided in a cylinder drum.
- the cylinder drum is supported on the front side on a swash plate whose angle of inclination determines the stroke of the piston.
- two oppositely oriented rows of pistons are provided in a solution disclosed in US Pat. No. 2,968,286, so that the axial piston machine is correspondingly formed with two cylindrical drums and two swash plates.
- the pistons are connected to a shaft which, depending on the design of the axial piston machine, acts as a drive or output shaft.
- the present invention seeks to provide an axial piston machine, the compensation transversal movements allowed with minimal device technical effort.
- the axial piston machine has a cylinder drum with a plurality of cylinder sleeves, which are supported directly or indirectly on a swash plate. This support is carried out according to the invention by means of a joint which is designed such that the transverse movements are compensated by a tilting movement of the cylinder sleeves. Due to the articulated mounting of the cylinder sleeves with respect to the swash plate, the risk of the formation of grooves or other grooves is minimal, so that the term of the axial piston machine is significantly extended compared to conventional solutions.
- the joint is designed as a universal or ball joint, which allows an all-round pivoting of the cylinder sleeves in the desired range.
- the ball joint has a hinge pin which passes through a bottom of the cylinder sleeve and forms the ball joint with an inner peripheral portion of the cylinder sleeve.
- this hinge pin is designed as a spherical cap, is formed on the crowned head of a voltage applied to the inner peripheral wall of the cylinder sleeve seal.
- the joint is in kinematic reversal by an axially from the bottom of Cylinder sleeve protruding pin formed whose free end portion dips into a receptacle of the swash plate or a voltage applied to the swash plate component, such as a driver and is mounted there sealing.
- the reliability of the axial piston machine according to the invention is improved when the cylinder sleeves are biased in the direction of the swash plate.
- this spring preload by means of a cylinder sleeve engaging spring, which engages a foot-side, radially projecting support edge of the cylinder sleeve.
- the bottom of the cylinder sleeve is designed to be spherical, so that it rolls when tilted on this crowned area.
- the cylinder sleeves are preferably guided on a driver of the cylinder drum, which is supported with an end face on the swash plate and is rotatably connected to the drive or output shaft. It is preferred if the driver has a drive plate with a flange, at the side remote from the swash plate annular end face, the cylinder sleeves are supported.
- kidney-shaped openings can be provided in the flange, in which these hinge pins are used.
- the dipping into the kidney-shaped openings part of the hinge pin can then be determined by crimping form-fitting.
- the hinge pins or the pins used in the kinematic reversal are preferably hollow, so that it can be guided by these pressure medium.
- the axial piston machine can be designed with two oppositely oriented rows of pistons, two cylinder drums and two swash plates.
- the pistons are designed in pairs as a double piston and are non-rotatably connected to a drive flange of the shaft.
- the dipping into the cylinder sleeve portions of the piston are conical, formed to gaskets towards enlarging.
- the construction according to the invention can be used particularly advantageously in axial piston pumps in which the shaft serves as a drive shaft for driving the pistons and the cylinder drums.
- FIG. 1 shows a longitudinal section through an axial piston pump 1.
- This has a pump housing 2, on which a not shown tank and a pressure port is formed.
- a drive shaft 4 is rotatably supported via a bearing assembly 6.
- a protruding from the pump housing 2 free end portion of the drive shaft 4 is connected to a drive motor, not shown.
- An inner bore 8 of the pump housing 2 accommodating the drive shaft 4 is expanded radially to form a pump chamber 10, in which two swash plates 12, 14 are mounted non-rotatably.
- the two swash plates 12, 14 each have an obliquely to the vertical in Fig. 1 extending support surface 16, on each of which a cylinder drum 18, 20 is supported.
- each cylinder drum 18, 20 has a plurality of cylinder sleeves 22, 23 in each of which a piston 24, 26 is immersed.
- the swash plates 12, 14 and correspondingly the cylinder drums 18, 20 arranged symmetrically to the vertically extending central axis M.
- the two pistons 24, 26 are each formed by the end portions of a double piston 28 which is rotatably inserted into a radially projecting drive flange 30 of the drive shaft 4.
- the storage of the cylinder drums 18, 20 via spherical bearings 32, 34 which allow the occurring due to the inclination of the cylinder drums 18, 20 during the rotation of the shaft 4 tumbling motion. Further details of the arrangement will be explained with reference to the detailed illustration of the cylinder drum 20 in FIG. 2.
- the cylinder drum 20 has a driver 36, which is supported on the drive shaft 4 via the joint 34 and which is slidably supported with a radially widened flange part 40 on the obliquely set support surface 16 of the swashplate 14.
- the self-aligning bearing 34 engages in an inner bore of a hub-shaped projection 38 of the driver 36.
- the tension spring 48 is in turn supported on a support ring 58 which engages around the outer circumference of the cylinder sleeves 23 and the hub-shaped projection 38 and is supported in the axial direction by means of a support means 52.
- the cylinder sleeve 23 has a cylinder bore 54 into which the piston forming the end portion of the double piston 28 dips.
- the radial support of the cylinder sleeve 23 takes place by means of a ball stud 56 formed as a spherical cap 56, which dips into the cylinder bore 54 with a crowned head 58 and sealingly abuts on the inner peripheral wall of the cylinder bore 54 via a seal 60.
- the spherical cap 56 is inserted into a receptacle 62 of the flange part 40 described below in greater detail.
- the spherical cap 56 has a bore 64, which opens into an opening 66 of the flange 40, so that pressure medium from the cylinder sleeve 23 and the piston 26 limited cylinder space to the swash plate 14 and can flow in the reverse direction.
- this connecting channels not shown, formed via which in dependence on the rotational position (inner, outer dead center) of the cylinder drum 18, a connection to the tank or the pressure port is made to lead pressure medium to the cylinder chamber or pressurized high pressure fluid to a consumer to lead.
- the receptacle 62 has a bore portion 66 into which the part of the spherical cap 56 extending away from the head 58 is inserted.
- the bore portion 66 terminates in a kidney-shaped widened opening 68 which extends along a radial segment of the pitch circle along which the cylinder sleeves 23 are arranged.
- the axial length of the part of the spherical cap 56 inserted in the bore section 66 is selected such that an end section 70 protrudes into the opening 68.
- the fastening of the spherical cap 56 is then carried out by crimping these projecting into the kidney-shaped projection 68 end portions (see section X-Y in Fig. 1).
- kidney-shaped openings 68 space is created by these kidney-shaped openings 68 to allow a positive connection of the spherical cap 56 with the driver 36.
- the width b of the kidney-shaped opening 68 corresponds to the diameter of the bore section 66.
- the piston 26 is approximately conical, with its diameter starting from a waist 72 starting at a foot side, acting as a seal piston ring 74 flared and tapered after the piston ring 74 to an end face 76 again spherically is.
- the cone angle is chosen so that the peripheral surfaces of the piston 26 in the two dead centers (see Fig. 1 above: outer dead center, bottom 1: inner dead center) do not collide with the inner peripheral surfaces of the cylinder sleeves 22, 23 and just to this abutment, whereby in these end positions the seal must be ensured by the piston ring 74.
- the geometry of the arrangement according to the invention is chosen so that the cylinder sleeves 22, 23 are each aligned at the inner dead center vertically with respect to the end face 16 of the swash plate, so that the tilt angle at the inner dead center, d. H. during the pressure build-up minimal and thus a symmetrical support of the cylinder sleeves 22, 23 is ensured.
- Fig. 3 shows a partial view of another embodiment of an axial piston pump 1, in which only a cylinder drum 18 is shown.
- the further Zylindertrommmel 20 is executed in a corresponding manner.
- the embodiment shown in Fig. 3 differs from the above-described embodiments substantially in the storage of the cylinder sleeves 22.
- the structure of the double piston 28, the swash plates 12, 14 and the basic structure of the driver 36 is substantially identical, so that will be discussed below only on the different components.
- the cylinder sleeve 22 has a planar bottom surface 78, from which a pin 80 projects in the axial direction to the swash plate 12 out.
- the pin 80 has at its free end portion a head 58 with a seal 60, whose construction corresponds substantially to that of the above-described embodiment.
- the head 58 dips into a ball socket formed as a bearing receiver 82 and is biased by the tension spring 48 in this engaged position in which the spherical portions of the head 58 and the bearing seat 82 abut each other and thus form a universal joint.
- the end face 78 is arranged at a distance from the adjacent annular end face 42 of the driver 36, so that the sleeve to compensate for the transverse movement about the universal joint (82, 58) can tilt.
- a swash plate 12, 14 is shown with a constant angle of attack.
- this angle of attack for changing the stroke may also be variable.
- an axial piston machine with at least one swash plate and a cylinder drum supported thereon, which has a plurality of cylinder sleeves.
- the cylinder sleeves is associated with a row of pistons, which is connected to a shaft. According to the cylinder sleeves are hinged in the cylinder drum.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
- Pistons, Piston Rings, And Cylinders (AREA)
Abstract
Description
Die Erfindung betrifft eine Axialkolbenmaschine gemäß dem Oberbegriff des Patentanspruchs 1.The invention relates to an axial piston machine according to the preamble of patent claim 1.
Eine derartige, beispielsweise aus der US 2,968,286 bekannte Axialkolbenmaschine hat eine Vielzahl von etwa in Axialrichtung angeordneten Kolben, die in einer Zylindertrommel geführt sind. Die Zylindertrommel ist stirnseitig an einer Schrägscheibe abgestützt, deren Neigungswinkel den Hub der Kolben bestimmt. Zur Minimierung der in Axialrichtung auftretenden Kräfte sind bei einer in der US 2,968,286 offenbarten Lösung zwei entgegengesetzt ausgerichtete Kolbenreihen vorgesehen, so dass die Axialkolbenmaschine entsprechend mit zwei Zylindertrommeln und zwei Schrägscheiben ausgebildet ist. Die Kolben sind mit einer Welle verbunden, die je nach Ausführung der Axialkolbenmaschine als Antriebs- oder Abtriebswelle wirkt. Aufgrund der Schrägstellung der Zylindertrommel kommt es bei der Rotation der Kolben um die Wellenachse und der entsprechenden Drehbewegung der Zylindertrommel zu einer Transversalbewegung zwischen Kolben und Zylindertrommel. Diese Transversalbewegung wird bei der bekannten Lösung dadurch ausgeglichen, dass die Kolben über ein Universalgelenk (Kugelgelenk) in einem drehfest mit der Welle verbundenen Antriebsflansch gelagert sind.Such, for example, from US 2,968,286 known axial piston machine has a plurality of approximately axially arranged pistons, which are guided in a cylinder drum. The cylinder drum is supported on the front side on a swash plate whose angle of inclination determines the stroke of the piston. In order to minimize the forces occurring in the axial direction, two oppositely oriented rows of pistons are provided in a solution disclosed in US Pat. No. 2,968,286, so that the axial piston machine is correspondingly formed with two cylindrical drums and two swash plates. The pistons are connected to a shaft which, depending on the design of the axial piston machine, acts as a drive or output shaft. Due to the inclination of the cylinder drum occurs during the rotation of the piston about the shaft axis and the corresponding rotational movement of the cylinder drum to a transverse movement between the piston and the cylinder drum. This transverse movement is compensated in the known solution in that the pistons are mounted via a universal joint (ball joint) in a rotatably connected to the shaft drive flange.
In der WO 81/03677 A1 ist eine ähnliche Lösung mit entgegengesetzt gerichteten Kolbenreihen offenbart, bei der die Kolben paarweise mittels einer Verbindungsstange verbunden sind. Diese Verbindungsstange ist über ein Kugelgelenk und mit Spiel im Antriebsflansch gelagert und erlaubt ebenfalls den Ausgleich der transversalen Bewegungen.In WO 81/03677 A1 a similar solution with oppositely directed rows of pistons is disclosed in which the pistons are connected in pairs by means of a connecting rod. This connecting rod is mounted via a ball joint and with play in the drive flange and also allows the compensation of transversal movements.
In der WO 94/10443 A1 ist eine gattungsgemäße Lösung offenbart, bei der die Kolben starr mit dem Antriebsflansch verbunden sind und sich parallel zur Axialrichtung (Welle) erstrecken. Der Ausgleich der Transversalbewegungen erfolgt durch eine Ausbildung der Zylinder mit gekrümmten Umfangsflächen. Eine ähnliche Lösung ist auch in der US 5,636,561 offenbart.In WO 94/10443 A1, a generic solution is disclosed in which the pistons are rigidly connected to the drive flange and extend parallel to the axial direction (shaft). The compensation of the transverse movements takes place by forming the cylinders with curved peripheral surfaces. A similar solution is also disclosed in US 5,636,561.
Die vorgeschriebenen Lösungen haben den Nachteil gemeinsam, dass ein erheblicher vorrichtungstechnischer Aufwand zum Ausgleich der Transversalbewegungen erforderlich ist.The prescribed solutions have the common disadvantage that a considerable device-technical effort to compensate for the transversal movements is required.
In der US 3,648,567 ist eine Axialkolbenmaschine mit nur einer Kolbenreihe offenbart, die drehfest mit dem Antriebsflansch verbunden ist. Die parallel zur Axialrichtung vorstehenden Kolben tauchen in Hülsen der Zylindertrommel ein, die gleitend auf der Schrägscheibe geführt sind.In US 3,648,567 an axial piston machine is disclosed with only one row of pistons, which is rotatably connected to the drive flange. The pistons protruding parallel to the axial direction dip into sleeves of the cylinder drum, which are slidably guided on the swash plate.
Der Nachteil einer derartigen Lösung besteht darin, dass die Anlageflächen zwischen den Hülsen und der Schrägscheibe äußerst exakt bearbeitet werden müssen. Des Weiteren kann es durch das Abgleiten der Hülsen bei ungünstigen Betriebsbedingungen zu der Ausbildung von Riefen in der Schrägscheibe oder in den Hülsen kommen. Insbesondere bei schnellen Lastwechseln können die Hülsen kippen, so dass die Gefahr einer Beschädigung besteht und so Leistungsverluste in Kauf genommen werden müssen.The disadvantage of such a solution is that the contact surfaces between the sleeves and the swash plate must be processed extremely accurately. Furthermore, the sliding of the sleeves in unfavorable operating conditions can lead to the formation of grooves in the swash plate or in the sleeves. In particular, during rapid load changes, the sleeves can tilt, so there is a risk of damage and so losses in performance must be accepted.
Demgegenüber liegt der Erfindung die Aufgabe zugrunde, eine Axialkolbenmaschine zu schaffen, die den Ausgleich transversaler Bewegungen mit minimalem vorrichtungstechnischem Aufwand erlaubt.In contrast, the present invention seeks to provide an axial piston machine, the compensation transversal movements allowed with minimal device technical effort.
Diese Aufgabe wird durch eine Axialkolbenmaschine mit den Merkmalen des Patentanspruchs 1 gelöst.This object is achieved by an axial piston machine having the features of patent claim 1.
Erfindungsgemäß hat die Axialkolbenmaschine eine Zylindertrommel mit einer Vielzahl von Zylinderhülsen, die direkt oder mittelbar an einer Schrägscheibe abgestützt sind. diese Abstützung erfolgt erfindungsgemäß mittels eines Gelenks, das derart ausgestaltet ist, dass die Transversalbewegungen durch eine Kippbewegung der Zylinderhülsen ausgeglichen werden. Durch die gelenkige Lagerung der Zylinderhülsen mit Bezug zur Schrägscheibe ist die Gefahr des Ausbildens von Riefen oder sonstiger Laufrillen minimal, so dass die Laufzeit der Axialkolbenmaschine gegenüber herkömmlichen Lösungen wesentlich verlängert ist.According to the invention, the axial piston machine has a cylinder drum with a plurality of cylinder sleeves, which are supported directly or indirectly on a swash plate. this support is carried out according to the invention by means of a joint which is designed such that the transverse movements are compensated by a tilting movement of the cylinder sleeves. Due to the articulated mounting of the cylinder sleeves with respect to the swash plate, the risk of the formation of grooves or other grooves is minimal, so that the term of the axial piston machine is significantly extended compared to conventional solutions.
Erfindungsgemäß wird es bevorzugt, wenn das Gelenk als Universal- oder Kugelgelenk ausgebildet ist, das eine allseitige Verschwenkung der Zylinderhülsen im gewünschten Bereich ermöglicht.According to the invention it is preferred if the joint is designed as a universal or ball joint, which allows an all-round pivoting of the cylinder sleeves in the desired range.
Bei einem besonders bevorzugten Ausführungsbeispiel hat das Kugelgelenk einen Gelenkbolzen, der einen Boden der Zylinderhülse durchsetzt und mit einem Innenumfangsbereich der Zylinderhülse das Kugelgelenk ausbildet.In a particularly preferred embodiment, the ball joint has a hinge pin which passes through a bottom of the cylinder sleeve and forms the ball joint with an inner peripheral portion of the cylinder sleeve.
Bei einer besonders einfachen Variante ist dieser Gelenkbolzen als Kugelkalotte ausgeführt, an deren balligem Kopf eine an der Innenumfangswandung der Zylinderhülse anliegende Dichtung ausgebildet ist.In a particularly simple variant of this hinge pin is designed as a spherical cap, is formed on the crowned head of a voltage applied to the inner peripheral wall of the cylinder sleeve seal.
Bei einer alternativen Variante wird das Gelenk in kinematischer Umkehrung durch einen axial vom Boden der Zylinderhülse vorstehenden Zapfen gebildet, dessen freier Endabschnitt in eine Aufnahme der Schrägscheibe oder eines an der Schrägscheibe anliegenden Bauelementes, beispielsweise eines Mitnehmers eintaucht und dort dichtend gelagert ist.In an alternative variant, the joint is in kinematic reversal by an axially from the bottom of Cylinder sleeve protruding pin formed whose free end portion dips into a receptacle of the swash plate or a voltage applied to the swash plate component, such as a driver and is mounted there sealing.
Die Funktionssicherheit der erfindungsgemäßen Axialkolbenmaschine wird verbessert, wenn die Zylinderhülsen in Richtung zur Schrägscheibe vorgespannt sind.The reliability of the axial piston machine according to the invention is improved when the cylinder sleeves are biased in the direction of the swash plate.
Bei eines besonders einfach herstellbaren Variante der Erfindung erfolgt diese Federvorspannung mittels einer die Zylinderhülse umgreifenden Feder, die an einem fußseitigen, radial vorstehenden Stützrand der Zylinderhülse angreift.In a particularly easy to manufacture variant of the invention, this spring preload by means of a cylinder sleeve engaging spring, which engages a foot-side, radially projecting support edge of the cylinder sleeve.
Bei einem Ausführungsbeispiel ist der Boden der Zylinderhülse ballig ausgeführt, so dass diese beim Kippen auf diesem balligen Bereich abrollt.In one embodiment, the bottom of the cylinder sleeve is designed to be spherical, so that it rolls when tilted on this crowned area.
Die Zylinderhülsen sind vorzugsweise an einem Mitnehmer der Zylindertrommel geführt, der mit einer Stirnfläche an der Schrägscheibe abgestützt ist und der drehfest mit der Antriebs- oder Abtriebswelle verbunden ist. Dabei wird es bevorzugt, wenn der Mitnehmer eine Mitnehmerscheibe mit einem Flanschteil hat, an dessen von der Schrägscheibe abgewandten Ringstirnfläche die Zylinderhülsen abgestützt sind.The cylinder sleeves are preferably guided on a driver of the cylinder drum, which is supported with an end face on the swash plate and is rotatably connected to the drive or output shaft. It is preferred if the driver has a drive plate with a flange, at the side remote from the swash plate annular end face, the cylinder sleeves are supported.
Für den Fall, dass die Zylinderhülsen mittels Gelenkbolzen gelagert sind, können im Flanschteil nierenförmige Durchbrüche vorgesehen werden, in die diese Gelenkbolzen eingesetzt werden. Der in die nierenförmigen Durchbrüche eintauchende Teil der Gelenkbolzen kann dann durch Umbördeln formschlüssig festgelegt werden.In the event that the cylinder sleeves are mounted by means of hinge pins, kidney-shaped openings can be provided in the flange, in which these hinge pins are used. The dipping into the kidney-shaped openings part of the hinge pin can then be determined by crimping form-fitting.
Die Gelenkbolzen oder die bei der kinematischen Umkehr verwendeten Zapfen werden vorzugsweise hohl ausgebildet, so dass durch diese Druckmittel geführt werden kann.The hinge pins or the pins used in the kinematic reversal are preferably hollow, so that it can be guided by these pressure medium.
Zur Minimierung der in Axialrichtung auftretenden Kräfte kann die Axialkolbenmaschine mit zwei entgegengesetzt ausgerichteten Kolbenreihen, zwei Zylindertrommeln und zwei Schrägscheiben ausgeführt sein.To minimize the forces occurring in the axial direction, the axial piston machine can be designed with two oppositely oriented rows of pistons, two cylinder drums and two swash plates.
Bei einer erfindungsgemäßen Lösung wird es bevorzugt, wenn die Kolben paarweise als Doppelkolben ausgeführt sind und drehfest mit einem Antriebsflansch der Welle verbunden sind. Die in die Zylinderhülse eintauchenden Abschnitte der Kolben sind konisch, sich zu Dichtungen hin vergrößernd ausgebildet.In a solution according to the invention, it is preferred if the pistons are designed in pairs as a double piston and are non-rotatably connected to a drive flange of the shaft. The dipping into the cylinder sleeve portions of the piston are conical, formed to gaskets towards enlarging.
Die erfindungsgemäße Konstruktion lässt sich besonders vorteilhaft bei Axialkolbenpumpen einsetzen, bei denen die Welle als Antriebswelle zum Antrieb der Kolben und der Zylindertrommeln dient.The construction according to the invention can be used particularly advantageously in axial piston pumps in which the shaft serves as a drive shaft for driving the pistons and the cylinder drums.
Sonstige vorteilhafte Weiterbildungen der Erfindung sind Gegenstand weiterer Unteransprüche.Other advantageous developments of the invention are the subject of further subclaims.
Im Folgenden wird ein bevorzugtes Ausführungsbeispiel der Erfindung anhand schematischer Zeichnungen näher erläutert. Es zeigen:
- Fig. 1 einen Schnitt durch ein erstes Ausführungsbeispiel einer erfindungsgemäßen Axialkolbenpumpe;
- Fig. 2 eine Detaildarstellung des Ausführungsbeispiels aus Fig. 1 und
- Fig. 3 eine Detaildarstellung eines weiteren Ausführungsbeispiels einer Axialkolbenpumpe.
- 1 shows a section through a first embodiment of an axial piston pump according to the invention.
- Fig. 2 is a detailed view of the embodiment of Fig. 1 and
- Fig. 3 is a detailed view of another embodiment of an axial piston pump.
Fig. 1 zeigt einen Längsschnitt durch eine Axialkolbenpumpe 1. Diese hat ein Pumpengehäuse 2, an dem ein nicht dargestellter Tank- und ein Druckanschluss ausgebildet ist. Im Pumpengehäuse 2 ist eine Antriebswelle 4 über eine Lageranordnung 6 drehbar gelagert. Ein aus dem Pumpengehäuse 2 vorstehender freier Endabschnitt der Antriebswelle 4 ist mit einem nicht dargestellten Antriebsmotor verbunden.1 shows a longitudinal section through an axial piston pump 1. This has a
Eine die Antriebswelle 4 aufnehmende Innenbohrung 8 des Pumpengehäuses 2 ist radial zu einem Pumpenraum 10 erweitert, in dem zwei Schrägscheiben 12, 14 drehfest gelagert sind. Die beiden Schrägscheiben 12, 14 haben jeweils eine schräg zur Vertikalen in Fig. 1 verlaufende Stützfläche 16, an der jeweils eine Zylindertrommel 18, 20 abgestützt ist. Wie im Folgenden noch näher erläutert wird, hat jede Zylindertrommel 18, 20 eine Vielzahl von Zylinderhülsen 22, 23 in die jeweils ein Kolben 24, 26 eintaucht. Wie der Darstellung gemäß Fig. 1 entnehmbar ist, sind die Schrägscheiben 12, 14 und entsprechend die Zylindertrommeln 18, 20 symmetrisch zur vertikal verlaufenden Mittelachse M angeordnet. Die beiden Kolben 24, 26 sind dabei jeweils durch die Endabschnitte eines Doppelkolbens 28 gebildet, der drehfest in einen radial vorspringenden Antriebsflansch 30 der Antriebswelle 4 eingesetzt ist. Die Lagerung der Zylindertrommeln 18, 20 erfolgt über Pendellager 32, 34 die die aufgrund der Schrägstellung der Zylindertrommeln 18, 20 während der Rotation der Welle 4 auftretende Taumelbewegung ermöglichen. Weitere Einzelheiten der Anordnung werden anhand der Detaildarstellung der Zylindertrommel 20 in Fig. 2 erläutert.An
Erfindungsgemäß hat die Zylindertrommel 20 einen über das Gelenk 34 an der Antriebswelle 4 abgestützten Mitnehmer 36, der mit einem radial erweiterten Flanschteil 40 auf der schräg angestellten Stützfläche 16 der Schrägscheibe 14 gleitend abgestützt ist. Die Pendellagerung 34 greift in einer Innenbohrung eines nabenförmigen Vorsprungs 38 des Mitnehmers 36 an.According to the invention, the cylinder drum 20 has a driver 36, which is supported on the
An einer von der Stützfläche 16 entfernten Ringstirnfläche 42 des Flanschteils 40 sind die gleichmäßig über den Umfang verteilten Zylinderhülsen 23 der Zylindertrommel 20 abgestützt. Diese haben fußseitig einen radial vorstehenden, umlaufenden Stützrand 44, dessen auf der Ringstirnfläche 42 aufliegende Bodenfläche 46 ballig ausgeführt ist, so dass die Zylinderhülse 23 eine allseitige Kippbewegung ausführen kann, wobei durch die ballige Bodenfläche 46 jeweils eine definierte Auflagefläche gewährleistet ist.On one of the
An dem Stützrand 44 greift eine Spannfeder 48 an, so dass die Zylinderhülse 23 in ihre Anlageposition gegen die Ringstirnfläche 42 vorgespannt ist. Die Spannfeder 48 ist ihrerseits an einem Stützring 58 abgestützt, der den Außenumfang der Zylinderhülsen 23 und den nabenförmigen Vorsprung 38 umgreift und in Axialrichtung mittels einer Stützeinrichtung 52 abgestützt ist. Die Zylinderhülse 23 hat eine Zylinderbohrung 54, in die der den Endabschnitt des Doppelkolbens 28 ausbildende Kolben eintaucht.At the
Die radiale Abstützung der Zylinderhülse 23 erfolgt mittels einer als Gelenkbolzen ausgebildeten Kugelkalotte 56, die mit einem balligen Kopf 58 in die Zylinderbohrung 54 eintaucht und über eine Dichtung 60 dichtend an der Innenumfangswandung der Zylinderbohrung 54 anliegt. die Kugelkalotte 56 ist in eine im Folgenden, noch näher beschriebene Aufnahme 62 des Flanschteils 40 eingesetzt.The radial support of the cylinder sleeve 23 takes place by means of a
Die Kugelkalotte 56 hat eine Bohrung 64, die in einem Durchbruch 66 des Flanschteils 40 mündet, so dass Druckmittel von dem von der Zylinderhülse 23 und dem Kolben 26 begrenzten Zylinderraum zur Schrägscheibe 14 und in umgekehrter Richtung strömen kann. In dieser sind nicht dargestellte Verbindungskanäle ausgebildet, über die in Abhängigkeit von der Drehposition (innerer, äußerer Totpunkt) der Zylindertrommel 18 eine Verbindung mit dem Tank- oder dem Druckanschluss hergestellt wird, um Druckmittel zum Zylinderraum zu führen oder mit Hochdruck beaufschlagtes Druckmittel zu einem Verbraucher zu leiten.The
Einzelheiten der Aufnahme 62 werden anhand der Ansichten "A" und "X-Y" in Fig. 1 erläutert.Details of the shot 62 will be explained with reference to the views "A" and "X-Y" in FIG.
Gemäß der Ansicht "X-Y" hat die Aufnahme 62 einen Bohrungsabschnitt 66, in den der sich von dem Kopf 58 weg erstreckende Teil der Kugelkalotte 56 eingesetzt ist. Der Bohrungsabschnitt 66 mündet in einem nierenförmig erweiterten Durchbruch 68, der sich entlang eines Radialsegments desjenigen Teilkreises erstreckt, entlang dem die Zylinderhülsen 23 angeordnet sind. Die Axiallänge des in dem Bohrungsabschnitt 66 eingesetzten Teils der Kugelkalotte 56 ist dabei so gewählt, dass ein Endabschnitt 70 in den Durchbruch 68 vorsteht. Die Befestigung der Kugelkalotte 56 erfolgt dann durch Umbördeln dieser in den nierenförmigen Vorsprung 68 vorstehenden Endabschnitte (s. Schnitt X-Y in Fig. 1).According to the view "X-Y", the receptacle 62 has a
Das heißt, durch diese nierenförmigen Durchbrüche 68 wird Raum geschaffen, um eine formschlüssige Verbindung der Kugelkalotte 56 mit dem Mitnehmer 36 zu ermöglichen.That is, space is created by these kidney-shaped
Die Breite b des nierenförmigen Durchbruchs 68 entspricht dabei dem Durchmesser des Bohrungsabschnitts 66.The width b of the kidney-shaped
Gemäß der Darstellung in Fig. 2 ist der Kolben 26 etwa kegelförmig ausgeführt, wobei sich sein Durchmesser von einer Taille 72 ausgehend zu einem fußseitig angeordneten, als Dichtung wirkenden Kolbenring 74 konisch erweitert und im Anschluss an den Kolbenring 74 zu einer Stirnfläche 76 wieder ballig verjüngt ist.According to the illustration in FIG. 2, the
Der Konuswinkel ist dabei so gewählt, dass die Umfangsflächen des Kolbens 26 in den beiden Totpunkten (s. Fig. 1 oben: äußerer Totpunkt; Fig. 1 unten: innerer Totpunkt) nicht mit den Innenumfangsflächen der Zylinderhülsen 22, 23 kollidieren und gerade an diesen anliegen, wobei auch in diesen Endpositionen die Abdichtung über den Kolbenring 74 gewährleistet sein muss.The cone angle is chosen so that the peripheral surfaces of the
Die Geometrie der erfindungsgemäßen Anordnung ist so gewählt, dass die Zylinderhülsen 22, 23 jeweils im inneren Totpunkt vertikal mit Bezug zur Stirnfläche 16 der Schrägscheibe ausgerichtet sind, so dass der Kippwinkel im inneren Totpunkt, d. h. beim Druckaufbau minimal und somit eine symmetrische Abstützung der Zylinderhülsen 22, 23 gewährleistet ist.The geometry of the arrangement according to the invention is chosen so that the
Fig. 3 zeigt eine Teilansicht eines weiteren Ausführungsbeispiels einer Axialkolbenpumpe 1, bei dem lediglich eine Zylindertrommel 18 dargestellt ist. Die weitere Zylindertrommmel 20 ist in entsprechender Weise ausgeführt. Das in Fig. 3 dargestellte Ausführungsbeispiel unterscheidet sich von den vorbeschriebenen Ausführungsbeispielen im wesentlichen in der Lagerung der Zylinderhülsen 22. Der Aufbau der Doppelkolben 28, der Schrägscheiben 12, 14 und der Grundaufbau des Mitnehmers 36 ist im wesentlichen identisch, so dass im Folgenden nur auf die unterschiedlichen Bauelemente eingegangen wird.Fig. 3 shows a partial view of another embodiment of an axial piston pump 1, in which only a
Bei dem in Fig. 3 dargestellten Ausführungsbeispiel hat die Zylinderhülse 22 eine eben ausgebildete Bodenfläche 78, von der ein Zapfen 80 in Axialrichtung zur Schrägscheibe 12 hin auskragt. Der Zapfen 80 hat an seinem freien Endabschnitt einen Kopf 58 mit einer Dichtung 60, dessen Aufbau im wesentlichen demjenigen des vorbeschriebenen Ausführungsbeispiels entspricht. Der Kopf 58 taucht in eine als Kugelpfanne ausgebildete Lageraufnahme 82 ein und wird über die Spannfeder 48 in diese Eingriffposition vorgespannt, in der die balligen Abschnitte des Kopfes 58 und der Lageraufnahme 82 aneinander anliegen und somit ein Universalgelenk ausbilden.In the embodiment shown in Fig. 3, the
Die Stirnfläche 78 ist dabei im Abstand zur benachbarten Ringstirnfläche 42 des Mitnehmers 36 angeordnet, so dass die Hülse zum Ausgleich der Transversalbewegung um das Universalgelenk (82, 58) kippen kann.The end face 78 is arranged at a distance from the adjacent annular end face 42 of the driver 36, so that the sleeve to compensate for the transverse movement about the universal joint (82, 58) can tilt.
Im übrigen entspricht dieses Ausführungsbeispiel dem vorbeschriebenen, so dass weitere Erläuterungen entbehrlich sind.Moreover, this embodiment corresponds to the above, so that further explanations are unnecessary.
Bei dem dargestellten Ausführungsbeispiel ist eine Schrägscheibe 12, 14 mit konstantem Anstellwinkel dargestellt. Selbstverständlich kann dieser Anstellwinkel zur Veränderung des Hubs auch variabel ausgebildet sein.In the illustrated embodiment, a
Die vorbeschriebene Konstruktion lässt sich auch bei einem Axialkolbenmotor oder auch bei einem Hydrotransformator in Axialbauweise einsetzen. Prinzipiell ist die dargestellte gelenkige Lagerung der Zylinderhülsen 22 auch bei Varianten mit nur einer Schrägscheibe und einer Zylindertrommel einsetzbar.The above-described construction can also be used in an axial piston motor or even in a hydraulic transformer in axial construction. In principle, the illustrated articulated mounting of the cylinder sleeves 22nd also applicable to variants with only one swash plate and one cylinder drum.
Offenbart ist eine Axialkolbenmaschine mit zumindest einer Schrägscheibe und einer daran abgestützten Zylindertrommel, die eine Vielzahl von Zylinderhülsen hat. Den Zylinderhülsen ist eine Kolbenreihe zugeordnet, die mit einer Welle verbunden ist. Erfindungsgemäß sind die Zylinderhülsen gelenkig in der Zylindertrommel gelagert.Disclosed is an axial piston machine with at least one swash plate and a cylinder drum supported thereon, which has a plurality of cylinder sleeves. The cylinder sleeves is associated with a row of pistons, which is connected to a shaft. According to the cylinder sleeves are hinged in the cylinder drum.
- 11
- Axialkolbenpumpeaxial piston pump
- 22
- Pumpengehäusepump housing
- 44
- Antriebswelledrive shaft
- 66
- Lagercamp
- 88th
- Innenbohrunginternal bore
- 1010
- Pumpenraumpump room
- 1212
- Schrägscheibeswash plate
- 1414
- Schrägscheibeswash plate
- 1616
- Stützflächesupport surface
- 1818
- Zylindertrommelcylinder drum
- 2020
- Zylindertrommelcylinder drum
- 22, 2322, 23
- Zylinderhülsecylinder sleeve
- 2424
- Kolbenpiston
- 2626
- Kolbenpiston
- 2828
- Doppelkolbendouble piston
- 3030
- Antriebsflanschdrive flange
- 3232
- Pendellageraligning bearing
- 3434
- Pendellageraligning bearing
- 3636
- Mitnehmertakeaway
- 3838
- Vorsprunghead Start
- 4040
- Flanschteilflange
- 4242
- RingstirnflächeAnnular face
- 4444
- Stützrandsupporting edge
- 4040
- Bodenflächefloor area
- 4848
- Spannfedertension spring
- 5050
- Stützringsupport ring
- 5252
- Stützeinrichtungsupport means
- 5454
- Zylinderbohrungbore
- 5656
- Kugelkalottespherical cap
- 5858
- Kopfhead
- 6060
- Dichtungpoetry
- 6262
- Aufnahmeadmission
- 6464
- Bohrungdrilling
- 6666
- Bohrungsabschnittbore section
- 6868
- Durchbruchbreakthrough
- 7070
- Endabschnittend
- 7272
- Taillewaist
- 7474
- Kolbenringpiston ring
- 7676
- Stirnflächeface
- 7878
- Bodenflächefloor area
- 8080
- Zapfenspigot
- 8282
- Lageraufnahmebearing seat
Claims (17)
- Axial-piston machine including at least one swash plate (12, 14) on which a cylinder drum (18, 20) is supported, wherein pistons (24, 26) are guided that are in operative connection with a shaft (4), wherein the axis of rotation of the cylinder drum (18, 20) is inclined relative to the axis of rotation of the pistons (24, 26), and wherein the cylinder drum (18, 20) has a multiplicity of cylinder sleeves (22, 23) indirectly or directly supported on the swash plate (12, 14),
characterized in that each cylinder sleeve (22, 23) is pivotally mounted through the intermediary of a joint (58, 54; 58, 82). - Axial-piston machine in accordance with claim 1, wherein the joint (58, 54; 58, 82) is a ball joint.
- Axial-piston machine in accordance with claim 1 or 2, wherein a joint pin (56) extends through a bottom of the cylinder sleeve (22, 23) and forms the joint jointly with an inner peripheral range (54) of the cylinder sleeve (22, 23).
- Axial-piston machine in accordance with claim 3, wherein the joint pin is a spherical shell (56), on the spherical head (58) of which a seal (60) contacting the inner peripheral wall (54) of the cylinder sleeve (22, 23) is formed.
- Axial-piston machine in accordance with claim 1 or 2, wherein a joint pin of the joint is formed by a pin (80) which axially projects from the bottom of the cylinder sleeves (22, 23) and carries a seal (60).
- Axial-piston machine in accordance with any one of the preceding claims, wherein the cylinder sleeves (22, 24) are biased into a position of contact.
- Axial-piston machine in accordance with claim 6, wherein the cylinder sleeves (22, 23) have on the foot side a radially projecting support rim (44) on which a tensioning spring (48) attacks.
- Axial-piston machine in accordance with claim 3 or 4, wherein each cylinder sleeve (22, 24) has a spherical bottom surface (46).
- Axial-piston machine in accordance with any one of the preceding claims, wherein the cylinder sleeves (22, 23) are guided in a drive member (36) of the cylinder drums (18, 20), which drive member is supported through one end face on the swash plate (12, 14) and is connected in rotation with the shaft (4) so as to admit a tumbling motion.
- Axial-piston machine in accordance with claim 8, wherein the drive member (36) has a drive member disc with a flange part (40), at the annular end face (42) of which the cylinder sleeves (22, 23) are supported.
- Axial-piston machine in accordance with claim 10 and 3 or 4, wherein through openings (66, 68) are arranged in the flange part (40), approximately in axial alignment with the cylinder sleeve (22, 23), in each of which one joint pin (56) is immobilized.
- Axial-piston machine in accordance with claim 11, wherein the through opening (68) is formed in a kidney shape in portions thereof, and the joint pin (56) is positively immobilized by beading the ranges adjacent these kidney-shaped portions (68).
- Axial-piston machine in accordance with claim 3 or 5, wherein a bore (64) extends through the joint pin (56) or the pin (80).
- Axial-piston machine in accordance with claim 5 or a claim appended thereto, wherein a spherical head (58) of the pin (80) is mounted in a bearing reception (82) of the flange part (40).
- Axial-piston machine in accordance with any one of the preceding claims mit two rows of oppositely oriented pistons (24, 26), to each of which a cylinder drum (18, 20) and a swash plate (12, 14) are associated.
- Axial-piston machine in accordance with any one of the preceding claims, wherein the piston has the form of a double piston with two oppositely oriented pistons (24, 26) that are connected in rotation with the shaft (4), and the portions of which plunging into the cylinder sleeves (22, 23) conically expand from a constriction (72) towards the piston rings (74).
- Axial-piston machine in accordance with any one of the preceding claims, wherein it is realized as an axial piston pump.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
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DE10259311 | 2002-12-18 | ||
DE10259311 | 2002-12-18 | ||
PCT/DE2003/004013 WO2004055369A1 (en) | 2002-12-18 | 2003-12-05 | Axial piston engine |
Publications (2)
Publication Number | Publication Date |
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EP1573200A1 EP1573200A1 (en) | 2005-09-14 |
EP1573200B1 true EP1573200B1 (en) | 2007-02-21 |
Family
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP03782132A Expired - Lifetime EP1573200B1 (en) | 2002-12-18 | 2003-12-05 | Axial piston engine |
Country Status (5)
Country | Link |
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US (1) | US7470116B2 (en) |
EP (1) | EP1573200B1 (en) |
AT (1) | ATE354729T1 (en) |
DE (2) | DE10393875D2 (en) |
WO (1) | WO2004055369A1 (en) |
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- 2003-12-05 US US10/540,113 patent/US7470116B2/en not_active Expired - Fee Related
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Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102010048553A1 (en) | 2010-10-14 | 2012-04-19 | Robert Bosch Gmbh | Drive shaft for hydraulic machine e.g. axial piston machine, has pair of metallic guide balls which are set on respective shaft portions, and connected at shaft stem |
DE102010052561A1 (en) | 2010-11-25 | 2012-05-31 | Robert Bosch Gmbh | Method for attaching pistons to drive shaft of hydraulic machine, involves compressing securing element for non-positive position securing of pistons in retainer |
Also Published As
Publication number | Publication date |
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US7470116B2 (en) | 2008-12-30 |
WO2004055369A1 (en) | 2004-07-01 |
ATE354729T1 (en) | 2007-03-15 |
DE50306608D1 (en) | 2007-04-05 |
EP1573200A1 (en) | 2005-09-14 |
US20060120881A1 (en) | 2006-06-08 |
DE10393875D2 (en) | 2005-08-18 |
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