EP1590569B1 - Axial piston engine and a control plate for an axial piston engine - Google Patents

Axial piston engine and a control plate for an axial piston engine Download PDF

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Publication number
EP1590569B1
EP1590569B1 EP03788997A EP03788997A EP1590569B1 EP 1590569 B1 EP1590569 B1 EP 1590569B1 EP 03788997 A EP03788997 A EP 03788997A EP 03788997 A EP03788997 A EP 03788997A EP 1590569 B1 EP1590569 B1 EP 1590569B1
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EP
European Patent Office
Prior art keywords
control plate
control
axial piston
piston engine
cylinder drum
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
Application number
EP03788997A
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German (de)
French (fr)
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EP1590569A1 (en
Inventor
Josef Beck
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bosch Rexroth AG
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Brueninghaus Hydromatik GmbH
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Publication of EP1590569A1 publication Critical patent/EP1590569A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2021—Details or component parts characterised by the contact area between cylinder barrel and valve plate
    • 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
    • F04B1/2042—Valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18056—Rotary to or from reciprocating or oscillating
    • Y10T74/18344—Unbalanced weights

Definitions

  • the invention relates to an axial piston machine and a control plate for an axial piston machine.
  • pistons which are arranged so as to be longitudinally displaceable in cylinder bores of a cylinder drum execute a lifting movement with each revolution of the cylinder drum.
  • the movement consists of a suction stroke and a pressure stroke.
  • a control plate is used on the end face of the cylinder drum, which with kidney-shaped control openings enables the connection of the cylinder drum with a high-pressure connection or a low-pressure connection.
  • control plate is z. B. in the DE 43 40 061 A1 described.
  • the control plate has an outer diameter which corresponds to the inner diameter of the housing component.
  • the control plate In the direction of the side facing away from the cylinder drum, the control plate is supported on a housing cover.
  • a high pressure port and a low pressure port are formed, which open into corresponding control openings of the control plate.
  • the control plate In addition to the control openings, the control plate has a central recess, which is penetrated by a shaft which is non-rotatably connected to the cylinder drum.
  • control plate is centered at its outer edge in the housing and must be processed by the full-surface support of the control plate on the housing cover with a high surface quality, the losses of the axial piston machine keep low. Due to the large surfaces to be machined in a machining process, the material used, which is required in the blank of the control plate, considerable. In addition, a large outer diameter of the control plate is required by the centering of the control plate at its outer periphery, which ultimately leads to a high component weight.
  • a further disadvantage is that the unavoidable between the end face of the cylinder drum and the control plate pressure medium losses, which collect in the interior of the cylinder drum in a gap formed between the cylinder drum and the shaft, can not perform pressure equalization in the direction of the remaining leakage volume and thus during operation the axial piston machine builds up an increased pressure in this inner leakage volume.
  • the invention has for its object to provide an axial piston machine and a control plate for an axial piston machine, wherein the proportion of the machining processing is reduced and which has a lower component weight.
  • control plate according to the invention according to claim 1 and the axial piston machine according to the invention according to claim 8.
  • the centering of the control plate at its inner edge For this purpose, a centering surface is formed on the inner edge, which consists of several partial surfaces. These faces center the control plate on a corresponding centering, which is formed or fixed on sides of the housing.
  • the centering surface of three partial surfaces, which are formed by radial expansion of segments of the inner edge.
  • the radial extension of the inner edge in the region of individual, separate segments is in particular so large that between the centering and the control plate, a gap is formed, which is adapted to let pass the accumulated inside the cylinder drum leakage fluid.
  • a groove may be provided which extends in the radial direction, and thus connects the inner leakage volume with an outer leakage volume formed by the rest of the housing interior.
  • Fig. 1 shows an axial piston machine, which has a rotatably mounted in a housing 2 shaft 3, on which a cylinder drum 4 is arranged, wherein the cylinder drum 4 and the shaft 3 are rotatably connected to each other.
  • the shaft 3 penetrates the cylinder drum 4 and is mounted on both sides of the cylinder drum 4 in each case a rolling bearing 5 and 6.
  • the rolling bearing 6 has an outer bearing ring 7, which is inserted into a corresponding recess of a housing cover 8.
  • a plurality of cylinder bores 9 are formed, wherein the central axes of the cylinder bores 9 extend parallel to the central axis of the shaft 3.
  • axially displaceable piston 10 are used, which on the side facing away from the housing cover 8 side have a spherical head 11 which cooperates with a corresponding recess of a shoe 12 to a hinge connection.
  • the piston 10 is supported on a swash plate 13.
  • the pistons 10 Upon rotation of the cylinder drum 4, the pistons 10 therefore execute a stroke movement in the cylinder bores 9.
  • the height of the Hubs is determined by the position of the swash plate 13, wherein the position of the swash plate 13 is adjustable in the embodiment by a Stellvoraum 14.
  • the cylinder drum 4 has a central opening 15, in which a compression spring 16 is arranged, which is stretched between a first spring bearing 17 and a second spring bearing 18.
  • the first spring bearing 17 is fixed by the shaft 3 in the axial direction
  • the second spring bearing 18, however, is formed in the illustrated embodiment by an inserted into a groove of the cylinder drum 4 Seeger ring. Due to the force of the compression spring 16, therefore, the cylinder drum 4 is shifted in the axial direction so far that it rests sealingly with its end face 19 on a control plate 20.
  • the section shown in the Fig. 1 The axial piston machine 1 unrecognizable control openings of the control plate 20 are on their side remote from the cylinder drum 4 side in permanent contact with at least one high-pressure or low-pressure connection.
  • a high-pressure or low-pressure connection is exemplary in Fig. 2 represented and provided with the reference numerals 26 and 26 '.
  • the cylinder bores 9 are open via openings 21 to the end face 19 of the cylinder drum 4.
  • the openings 21 sweep with a rotation of the cylinder drum 4, a sealing environment 27 of the control plate 20 and are connected during a rotation alternately with the control ports of the high-pressure or low-pressure connection.
  • the end face 19 and the sealing surrounding tight sealing environment 27 may also be formed with a corresponding spherical shape.
  • the determination of the position of the control plate 20 is effected by a centering surface 29, which consists of a plurality of partial surfaces, as described below with reference to Fig. 3 yet is explained in detail.
  • the passage opening 38 of the control plate 20 has a radial extent, which corresponds to the outer radial extent of a centering body, wherein the centering body is connected to a housing component.
  • the inner diameter of the through hole and thus the centering surface 29 corresponds to the outer diameter of the outer bearing ring 7 of the rolling bearing 6 as centering, so that the control plate 20 is centered on the outer bearing ring 7.
  • the control plate 20 In the axial direction, the control plate 20 is supported on the housing cover 8.
  • the control plate 20 has a further sealing environment 28 which is formed on the side remote from the cylinder drum 4 side of the control plate 20 and which cooperates sealingly with the surface of the housing cover 8.
  • the central opening 15 of the cylinder drum 4 defines an internal leakage volume 44, which receives a portion of the leakage oil.
  • a gap 22 is formed between the control plate 20 and the outer bearing ring 7, which is connected by a groove 25 with the remaining housing volume 24. Via the gap 22 and the groove 25, therefore, the inner leakage volume is in contact with the outer leakage volume 45 of the remaining housing volume, so that a pressure compensation is possible.
  • the collected in the interior of the housing volume leakage fluid is supplied to the pressure medium circuit in a manner not shown again.
  • Fig. 2 the area of the control plate 20 is shown enlarged again, the sectional plane with respect the presentation Fig. 1 rotated by 90 °. Identical components are provided with identical reference numerals.
  • the cut now passes through the control plate 20 so that a first control opening 32 and a second control opening 33 can be seen.
  • the centering surface 29, with which the control plate 20 is supported at several points of the outer circumference of the outer bearing ring 7 is used.
  • another dowel 34 which is inserted into a bore of the housing cover 8 and engages in a corresponding groove in the control plate 20.
  • a radial extension 35 is formed on the outer edge 46 of the control plate 20 in order to cope with the higher mechanical loads on the high pressure side.
  • the outwardly radially widened region 35 and the inner edge 47 of the control plate 20 on which the centering surface 29 is formed, is reduced in thickness compared to the sealing environment 27 and the oppositely oriented further sealing environment 28. Since the inner edge 47 of the control plate 20 and the radial extension 35 on their surfaces, which are oriented in the direction of the cylinder drum 4 and in the direction of the housing cover 8 only low demands on the surface finish, in this area, a post-processing of the blank largely omitted. In contrast, in the region of the sealing environment 27 and the oppositely oriented further sealing environment 28, the blank of the control plate 20 is reworked accordingly, wherein a high surface quality and flatness is achieved, for example, by lapping.
  • FIG Fig. 3 An example of a structural design of a control plate 20 is shown in FIG Fig. 3 shown.
  • the control plate 20 has a substantially circular Geometry on.
  • a passage opening 38 is formed in the control plate 20, which has a diameter of d 1 .
  • the inner edge 47 of this passage opening 38 forms the centering surface 29.
  • the passage opening 38 is extended at individual recesses 36.1, 36.2 and 36.3 in the radial direction inwards. Between the recesses 36.1 to 36.3 in each case a segment 43.1, 43.2 and 43.3 with an inner diameter d 1 remains.
  • three partial surfaces 29.1, 29.2 and 29.3 are formed on the segments 43.1, 43.2 and 43.3 as the centering surface 29.
  • the third subarea 29.3 is subdivided once more by the introduction of a recess 37, so that the third subarea 29.3 consists of the two subareas designated 29.3 'and 29.3 ", correspondingly the third segment 43.3 consists of the two subsegments 43.3' and 43.3 ".
  • the recess 37 is provided for receiving the dowel 34, so that the control openings 32 and 33.1 to 33.5 have a defined position.
  • the recesses 36.1, 36.2 and 36.3 are distributed uniformly over the circumference of the passage opening 38. Its radial extension extends to a diameter d 2 , which is large enough to form to the outer bearing ring 7, the gap 22, which is passable by a leakage fluid.
  • the control plate 20 further includes the kidney-shaped low-pressure control port 32, via which the openings 21 of the cylinder drum 4 are connected to the low pressure port.
  • a plurality of likewise kidney-shaped high-pressure control openings are provided in the embodiment shown, which are designated by the reference numerals 33.1 to 33.5.
  • the respective adjacent high-pressure control openings 33.1 to 33.5 are separated by a separating web 39.1 to 39.4.
  • separating surfaces 41 and 42 are formed, which close the openings 21 with built-in control disk 20 in the region of the top and bottom dead center, as in Fig. 1 is shown.
  • a radial extension 35 is additionally formed in the region of the high-pressure control openings 33.1 to 33.5.
  • the radial extension 35 has an outer edge 40, which extends in a circular arc and which is formed concentrically to the circular disk-shaped geometry of the control plate 20.
  • the control plate 20 is made of a blank, which is preferably produced in a hot forging process.
  • the blank is in the region of the radial extension 35 and in the region between the diameters d 1 and d 2 of lesser thickness than in the sealing region 27 and 28.
  • the working out of the radial enlargement of the recesses 36.1, 36.2 and 36.3 already takes place in Hot forging process or by machining, as well as the introduction of the recess 37 for the other dowel 34.
  • the control ports 32 and 33.1 to 33.5 are preferably punched, the punching can be done in the warm or cold state.
  • the sealing environments 27 and 28 are processed by lapping, for example.
  • Fig. 4 is a section through the control plate 20 along the line IV - IV in Fig. 3 shown.
  • the sectional view can be seen again that in the area of the sealing environment 27 and the other sealing environment 28 of the control openings 32 and 33 has a greater thickness t 2 of the control plate 20 compared to the thickness t 1 in the region of the radial extension 35 and Centering surface 29 and the segments 43.1 to 43.3 is provided, wherein the thickness change preferably takes place on both sides of the control plate 20.
  • the proportion of machining reduces from about 50% to about 20%.
  • a further advantage is a shortening of the processing time.

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

Abstract

The invention relates to a control plate (20) for an axial piston engine (1). The inventive control plate (20) comprises a through hole (38) and a radial internal edge of said control plate (20) embodied in the form of a centring surface (29) which centres the control plate (20) to a centring body (7) arranged on the side of a bearing surface. Said centring surface (29) consists of several partial surfaces (29.1, 29.2, 29.3) formed on segments (43.1, 43.2, 43.3) of the internal edge (47) of the control plate (20) radially extending towards the internal space of said through hole (38). The segments (43.1, 43.2, 43.3) are divided by cuts (36.1, 36.2, 36.3).

Description

Die Erfindung betrifft eine Axialkolbenmaschine sowie eine Steuerplatte für eine Axialkolbenmaschine.The invention relates to an axial piston machine and a control plate for an axial piston machine.

Bei Axialkolbenmaschinen führen Kolben, die in Zylinderbohrungen einer Zylindertrommel längsverschieblich angeordnet sind, bei jeder Umdrehung der Zylindertrommel eine Hubbewegung aus. Die Bewegung besteht aus einem Saughub sowie einem Druckhub. Um eine drehsynchrone Verbindung zwischen der Zylindertrommel und der entsprechenden Arbeitsleitung der Axialkolbenmaschine zu erreichen, wird an der Stirnseite der Zylindertrommel eine Steuerplatte eingesetzt, welche mit nierenförmigen Steueröffnungen die Verbindung der Zylindertrommel mit einem Hochdruckanschluss bzw. einem Niederdruckanschluss ermöglicht.In the case of axial piston machines, pistons which are arranged so as to be longitudinally displaceable in cylinder bores of a cylinder drum execute a lifting movement with each revolution of the cylinder drum. The movement consists of a suction stroke and a pressure stroke. In order to achieve a rotationally synchronized connection between the cylinder drum and the corresponding working line of the axial piston machine, a control plate is used on the end face of the cylinder drum, which with kidney-shaped control openings enables the connection of the cylinder drum with a high-pressure connection or a low-pressure connection.

Eine solche Steuerplatte ist z. B. in der DE 43 40 061 A1 beschrieben. Die Steuerplatte weist einen äußeren Durchmesser auf, welcher mit dem Innendurchmesser des Gehäusebauteils korrespondiert. In Richtung der von der Zylindertrommel abgewandten Seite stützt sich die Steuerplatte an einem Gehäusedeckel ab. In dem Gehäusedeckel sind ein Hochdruckanschluss sowie ein Niederdruckanschluss ausgebildet, welche in entsprechende Steueröffnungen der Steuerplatte ausmünden. Neben den Steueröffnungen weist die Steuerplatte eine zentrale Ausnehmung auf, die von einer Welle, die drehfest mit der Zylindertrommel verbunden ist, durchdrungen ist. Der Gegenstand des Anspruchs 1 ist in zweiteiliger Form gegenüber dieser Druckschrift abgegrenzt.Such a control plate is z. B. in the DE 43 40 061 A1 described. The control plate has an outer diameter which corresponds to the inner diameter of the housing component. In the direction of the side facing away from the cylinder drum, the control plate is supported on a housing cover. In the housing cover, a high pressure port and a low pressure port are formed, which open into corresponding control openings of the control plate. In addition to the control openings, the control plate has a central recess, which is penetrated by a shaft which is non-rotatably connected to the cylinder drum. The subject matter of claim 1 is delimited in two-part form with respect to this document.

Nachteilig dabei ist, dass die Steuerplatte an ihrem äußeren Rand in dem Gehäuse zentriert wird und durch die vollflächige Auflage der Steuerplatte auf dem Gehäusedeckel mit einer hohen Oberflächengüte bearbeitet werden muss, um die Verluste der Axialkolbenmaschine gering zuhalten. Durch die großen, in einem spanenden Verfahren zu bearbeitenden Flächen ist der Materialeinsatz, welcher bei dem Rohteil der Steuerplatte erforderlich ist, erheblich. Zudem ist durch die Zentrierung der Steuerplatte an ihrem äußeren Umfang ein großer Außendurchmesser der Steuerplatte erforderlich, was letztlich zu einem hohen Bauteilgewicht führt.The disadvantage here is that the control plate is centered at its outer edge in the housing and must be processed by the full-surface support of the control plate on the housing cover with a high surface quality, the losses of the axial piston machine keep low. Due to the large surfaces to be machined in a machining process, the material used, which is required in the blank of the control plate, considerable. In addition, a large outer diameter of the control plate is required by the centering of the control plate at its outer periphery, which ultimately leads to a high component weight.

Weiterhin ist nachteilig, dass die zwischen der Stirnseite der Zylindertrommel und der Steuerplatte unvermeidbaren Druckmittelverluste, welche sich im Inneren der Zylindertrommel in einem zwischen der Zylindertrommel und der Welle ausgebildeten Spalt sammeln, keinen Druckausgleich in Richtung des übrigen Leckagevolumens ausführen können und sich damit während des Betriebs der Axialkolbenmaschine ein erhöhter Druck in diesem inneren Leckagevolumen aufbaut.A further disadvantage is that the unavoidable between the end face of the cylinder drum and the control plate pressure medium losses, which collect in the interior of the cylinder drum in a gap formed between the cylinder drum and the shaft, can not perform pressure equalization in the direction of the remaining leakage volume and thus during operation the axial piston machine builds up an increased pressure in this inner leakage volume.

Der Erfindung liegt die Aufgabe zugrunde, eine Axialkolbenmaschine sowie eine Steuerplatte für eine Axialkolbenmaschine zu schaffen, bei der der Anteil der spanenden Verarbeitung reduziert ist und welche ein geringeres Bauteilgewicht aufweist.The invention has for its object to provide an axial piston machine and a control plate for an axial piston machine, wherein the proportion of the machining processing is reduced and which has a lower component weight.

Die Aufgabe wird durch die erfindungsgemäße Steuerplatte nach Anspruch 1 sowie die erfindungsgemäße Axialkolbenmaschine nach Anspruch 8 gelöst.The object is achieved by the control plate according to the invention according to claim 1 and the axial piston machine according to the invention according to claim 8.

Erfindungsgemäß erfolgt die Zentrierung der Steuerplatte an deren innerem Rand. An dem inneren Rand ist hierfür eine Zentrierfläche ausgebildet, welche aus mehreren Teilflächen besteht. Diese Teilflächen zentrieren die Steuerplatte auf einem entsprechenden Zentrierkörper, welcher auf Seiten des Gehäuses ausgebildet bzw. fixiert ist. Durch die Zentrierung der Steuerplatte an deren innerem Rand kann der Außendurchmesser der Steuerplatte reduziert werden. Neben der unmittelbaren Reduzierung des Materialeinsatzes bei dem Rohteil zur Herstellung der Steuerplatte werden zudem auch Kosten dadurch reduziert, dass der Anteil an zu bearbeitenden Flächen der Steuerplatte gering ist.According to the invention, the centering of the control plate at its inner edge. For this purpose, a centering surface is formed on the inner edge, which consists of several partial surfaces. These faces center the control plate on a corresponding centering, which is formed or fixed on sides of the housing. By centering the control plate at the inner edge of the outer diameter of the control plate can be reduced. In addition to the immediate reduction of the use of material in the blank for the production of the control plate also costs are thereby reduced, that the proportion of surfaces to be machined of the control plate is low.

Die Unteransprüche betreffen vorteilhafte Weiterbildungen der erfindungsgemäßen Steuerplatte bzw. der erfindungsgemäßen Axialkolbenmaschine.The dependent claims relate to advantageous developments of the control plate or the axial piston machine according to the invention.

Insbesondere ist es vorteilhaft, die Zentrierfläche aus drei Teilflächen zu bilden, welche durch radiale Erweiterung von Segmenten des inneren Rands gebildet werden. Die radiale Erweiterung des inneren Rands im Bereich einzelner, voneinander getrennter Segmente ist dabei insbesondere so groß, dass zwischen dem Zentrierkörper und der Steuerplatte ein Spalt ausgebildet wird, welcher geeignet ist, das im Inneren der Zylindertrommel angesammelte Leckagefluid passieren zu lassen.In particular, it is advantageous to form the centering surface of three partial surfaces, which are formed by radial expansion of segments of the inner edge. The radial extension of the inner edge in the region of individual, separate segments is in particular so large that between the centering and the control plate, a gap is formed, which is adapted to let pass the accumulated inside the cylinder drum leakage fluid.

Weiterhin kann vorteilhaft im Bereich der Trennflächen der Steuerplatte auf der von der Zylindertrommel abgewandten Seite der Steuerplatte oder in dem Gehäusedeckel eine Nut vorgesehen sein, welche in radialer Richtung verläuft, und somit das innere Leckagevolumen mit einem durch den übrigen Gehäuseinnenraum gebildeten äußeren Leckagevolumen verbindet. Mittels einer solchen Verbindung wird während des Betriebs der Axialkolbenmaschine ein permanenter Druckausgleich zwischen dem inneren Leckagevolumen und dem äußeren Leckagevolumen der Axialkolbenmaschine gewährleistet.Furthermore, advantageously in the region of the separating surfaces of the control plate on the side facing away from the cylinder drum side of the control plate or in the housing cover a groove may be provided which extends in the radial direction, and thus connects the inner leakage volume with an outer leakage volume formed by the rest of the housing interior. By means of such a connection, a permanent pressure equalization between the inner leakage volume and the outer leakage volume of the axial piston machine is ensured during operation of the axial piston machine.

Die erfindungsgemäße Steuerplatte sowie die erfindungsgemäße Axialkolbenmaschine sind in der Zeichnung dargestellt und werden anhand der nachfolgenden Beschreibung näher erläutert. Es zeigen:

Fig. 1
eine schematische Darstellung einer erfindungsgemäßen Axialkolbenmaschine;
Fig. 2
eine vergrößerte Darstellung des Bereichs der Steuerplatte der erfindungsgemäßen Axialkolbenmaschine;
Fig. 3
eine Aufsicht auf eine erfindungsgemäße Steuerplatte; und
Fig. 4
einen Schnitt einer erfindungsgemäßen Steuerplatte.
The control plate according to the invention and the axial piston according to the invention are shown in the drawing and will be explained in more detail with reference to the following description. Show it:
Fig. 1
a schematic representation of an axial piston machine according to the invention;
Fig. 2
an enlarged view of the area of the control plate of the axial piston machine according to the invention;
Fig. 3
a plan view of a control plate according to the invention; and
Fig. 4
a section of a control plate according to the invention.

Bevor auf die Einzelheiten der erfindungsgemäßen Axialkolbenmaschine bzw. der erfindungsgemäßen Steuerplatte eingegangen wird, sollen zunächst die wesentlichen Bauteile einer Axialkolbenmaschine, sowie deren Funktion zum besseren Verständnis der Erfindung erläutert werden. Fig. 1 zeigt eine Axialkolbenmaschine, welche eine in einem Gehäuse 2 drehbar gelagerte Welle 3 aufweist, auf der eine Zylindertrommel 4 angeordnet ist, wobei die Zylindertrommel 4 und die Welle 3 miteinander drehfest verbunden sind. Die Welle 3 durchdringt die Zylindertrommel 4 und ist auf beiden Seiten der Zylindertrommel 4 in jeweils einem Wälzlager 5 und 6 gelagert. Das Wälzlager 6 weist einen äußeren Lagerring 7 auf, der in eine entsprechende Ausnehmung eines Gehäusedeckels 8 eingesetzt ist.Before discussing the details of the axial piston machine according to the invention or the control plate according to the invention, the essential components of an axial piston machine, as well as their function for better understanding of the invention will be explained first. Fig. 1 shows an axial piston machine, which has a rotatably mounted in a housing 2 shaft 3, on which a cylinder drum 4 is arranged, wherein the cylinder drum 4 and the shaft 3 are rotatably connected to each other. The shaft 3 penetrates the cylinder drum 4 and is mounted on both sides of the cylinder drum 4 in each case a rolling bearing 5 and 6. The rolling bearing 6 has an outer bearing ring 7, which is inserted into a corresponding recess of a housing cover 8.

In der Zylindertrommel 4 sind über den Umfang verteilt mehrere Zylinderbohrungen 9 ausgebildet, wobei die Mittelachsen der Zylinderbohrungen 9 parallel zu der Mittelachse der Welle 3 verlaufen. In den Zylinderbohrungen 9 sind axialverschieblich Kolben 10 eingesetzt, welche an der von dem Gehäusedeckel 8 abgewandten Seite einen kugelförmigen Kopf 11 aufweisen, der mit einer korrespondierenden Ausnehmung eines Gleitschuhs 12 zu einer Gelenkverbindung zusammenwirkt. Mittels des Gleitschuhs 12 stützt sich der Kolben 10 an einer Schrägscheibe 13 ab. Bei einer Drehung der Zylindertrommel 4 führen die Kolben 10 daher in den Zylinderbohrungen 9 eine Hubbewegung aus. Die Höhe des Hubs wird dabei durch die Stellung der Schrägscheibe 13 vorgegeben, wobei die Stellung der Schrägscheibe 13 im Ausführungsbeispiel durch eine Stellvorichtung 14 einstellbar ist.In the cylinder drum 4 distributed over the circumference a plurality of cylinder bores 9 are formed, wherein the central axes of the cylinder bores 9 extend parallel to the central axis of the shaft 3. In the cylinder bores 9 axially displaceable piston 10 are used, which on the side facing away from the housing cover 8 side have a spherical head 11 which cooperates with a corresponding recess of a shoe 12 to a hinge connection. By means of the slide shoe 12, the piston 10 is supported on a swash plate 13. Upon rotation of the cylinder drum 4, the pistons 10 therefore execute a stroke movement in the cylinder bores 9. The height of the Hubs is determined by the position of the swash plate 13, wherein the position of the swash plate 13 is adjustable in the embodiment by a Stellvorichtung 14.

Die Zylindertrommel 4 weist eine zentrale Öffnung 15 auf, in der eine Druckfeder 16 angeordnet ist, welche zwischen einem ersten Federlager 17 und einem zweiten Federlager 18 gespannt ist. Das erste Federlager 17 ist dabei seitens der Welle 3 in axialer Richtung fixiert, das zweite Federlager 18 dagegen wird im dargestellten Ausführungsbeispiel durch einen in eine Nut der Zylindertrommel 4 eingesetzten Seegerring gebildet. Durch die Kraft der Druckfeder 16 wird daher die Zylindertrommel 4 in axialer Richtung soweit verschoben, dass sie mit ihrer Stirnfläche 19 an einer Steuerplatte 20 dichtend anliegt.The cylinder drum 4 has a central opening 15, in which a compression spring 16 is arranged, which is stretched between a first spring bearing 17 and a second spring bearing 18. The first spring bearing 17 is fixed by the shaft 3 in the axial direction, the second spring bearing 18, however, is formed in the illustrated embodiment by an inserted into a groove of the cylinder drum 4 Seeger ring. Due to the force of the compression spring 16, therefore, the cylinder drum 4 is shifted in the axial direction so far that it rests sealingly with its end face 19 on a control plate 20.

Die im dargestellten Schnitt der Fig. 1 der Axialkolbenmaschine 1 nicht erkennbaren Steueröffnungen der Steuerplatte 20 stehen auf ihrer von der Zylindertrommel 4 abgewandten Seite in permanentem Kontakt mit zumindest einem Hochdruck- bzw. Niederdruckanschluss. Ein Hochdruck- bzw. Niederdruckanschluss ist beispielhaft in Fig. 2 dargestellt und mit den Bezugszeichen 26 und 26' versehen. Die Zylinderbohrungen 9 sind über Öffnungen 21 zu der Stirnfläche 19 der Zylindertrommel 4 hin offen. Die Öffnungen 21 überstreichen bei einer Rotation der Zylindertrommel 4 eine dichtende Umgebung 27 der Steuerplatte 20 und werden dabei während eines Umlaufs alternierend mit den Steueröffnungen des Hochdruck- bzw. Niederdruckanschlusses verbunden. Die Stirnfläche 19 und die dichtend daran anliegende dichtende Umgebung 27 können auch mit einer korrespondierenden sphärischen Form ausgebildet sein.The section shown in the Fig. 1 The axial piston machine 1 unrecognizable control openings of the control plate 20 are on their side remote from the cylinder drum 4 side in permanent contact with at least one high-pressure or low-pressure connection. A high-pressure or low-pressure connection is exemplary in Fig. 2 represented and provided with the reference numerals 26 and 26 '. The cylinder bores 9 are open via openings 21 to the end face 19 of the cylinder drum 4. The openings 21 sweep with a rotation of the cylinder drum 4, a sealing environment 27 of the control plate 20 and are connected during a rotation alternately with the control ports of the high-pressure or low-pressure connection. The end face 19 and the sealing surrounding tight sealing environment 27 may also be formed with a corresponding spherical shape.

Die Festlegung der Position der Steuerplatte 20 erfolgt durch eine Zentrierfläche 29, die aus mehreren Teilflächen besteht, wie nachfolgend unter Bezugnahme auf Fig. 3 noch ausführlich erläutert wird. Die Durchgangsöffnung 38 der Steuerplatte 20 weist eine radiale Ausdehnung auf, welche mit der äußeren radialen Ausdehnung eines Zentrierkörpers korrespondiert, wobei der Zentrierkörper mit einem Gehäusebauteil verbunden ist. Im dargestellten Ausführungsbeispiel korrespondiert der Innendurchmesser der Durchgangsöffnung und damit die Zentrierfläche 29 mit dem Außendurchmesser des äußeren Lagerrings 7 des Wälzlagers 6 als Zentrierkörper, so dass die Steuerplatte 20 auf dem äußeren Lagerring 7 zentriert wird. In axialer Richtung stützt sich die Steuerplatte 20 an dem Gehäusedeckel 8 ab. Zur Vermeidung von Leckage weist die Steuerplatte 20 eine weitere dichtende Umgebung 28 auf, welche auf der von der Zylindertrommel 4 abgewandten Seite der Steuerplatte 20 ausgebildet ist und die mit der Oberfläche des Gehäusedeckels 8 dichtend zusammenwirkt.The determination of the position of the control plate 20 is effected by a centering surface 29, which consists of a plurality of partial surfaces, as described below with reference to Fig. 3 yet is explained in detail. The passage opening 38 of the control plate 20 has a radial extent, which corresponds to the outer radial extent of a centering body, wherein the centering body is connected to a housing component. In the illustrated embodiment, the inner diameter of the through hole and thus the centering surface 29 corresponds to the outer diameter of the outer bearing ring 7 of the rolling bearing 6 as centering, so that the control plate 20 is centered on the outer bearing ring 7. In the axial direction, the control plate 20 is supported on the housing cover 8. To prevent leakage, the control plate 20 has a further sealing environment 28 which is formed on the side remote from the cylinder drum 4 side of the control plate 20 and which cooperates sealingly with the surface of the housing cover 8.

Trotz der Bearbeitung der Stirnfläche 19 der Zylindertrommel 4 sowie der dichtenden Umgebung 27 der Steuerplatte 20 mit Verfahren, die eine hohe Oberflächengüte ermöglichen, tritt eine Leckage zwischen der Zylindertrommel 4 und der Steuerplatte 20 auf, die auch zum Ausbilden eines Schmierfilms erforderlich ist. Die zentrale Öffnung 15 der Zylindertrommel 4 begrenzt ein inneres Leckagevolumen 44, das einen Teil des Lecköls aufnimmt. Um einen Druckaufbau in dem an sich abgeschlossenen inneren Leckagevolumen 44 zu verhindern, ist zwischen der Steuerplatte 20 und dem äußeren Lagerring 7 ein Spalt 22 ausgebildet, der mittels einer Nut 25 mit dem übrigen Gehäusevolumen 24 verbunden ist. Über den Spalt 22 sowie die Nut 25 steht daher das innere Leckagevolumen in Kontakt zu dem äußeren Leckagevolumen 45 des übrigen Gehäusevolumens, so dass ein Druckausgleich möglich ist. Das im Inneren des Gehäusevolumens gesammelte Leckagefluid wird auf nicht dargestellte Weise dem Druckmittelkreislauf wieder zugeführt.Despite the machining of the end surface 19 of the cylindrical drum 4 and the sealing environment 27 of the control plate 20 with methods that allow a high surface finish, leakage between the cylinder drum 4 and the control plate 20, which is also required for forming a lubricating film occurs. The central opening 15 of the cylinder drum 4 defines an internal leakage volume 44, which receives a portion of the leakage oil. In order to prevent a pressure build-up in the self-contained inner leakage volume 44, a gap 22 is formed between the control plate 20 and the outer bearing ring 7, which is connected by a groove 25 with the remaining housing volume 24. Via the gap 22 and the groove 25, therefore, the inner leakage volume is in contact with the outer leakage volume 45 of the remaining housing volume, so that a pressure compensation is possible. The collected in the interior of the housing volume leakage fluid is supplied to the pressure medium circuit in a manner not shown again.

In Fig. 2 ist der Bereich der Steuerplatte 20 noch einmal vergrößert dargestellt, wobei die Schnittebene bezüglich der Darstellung aus Fig. 1 um 90° gedreht ist. Identische Bauteile sind mit identischen Bezugszeichen versehen. Der Schnitt verläuft nunmehr so durch die Steuerplatte 20, dass eine erste Steueröffnung 32 und eine zweite Steueröffnung 33 zu erkennen sind. Zur richtigen Positionierung der Steuerplatte 20 in radialer Richtung dient die Zentrierfläche 29, mit welcher sich die Steuerplatte 20 an mehreren Stellen des äußeren Umfangs des äußeren Lagerrings 7 abstützt. Zur Sicherung gegen Verdrehung dient im dargestellten Ausführungsbeispiel ein weiterer Paßstift 34, der in eine Bohrung des Gehäusedeckels 8 eingesetzt ist und in eine korrespondierende Nut in der Steuerplatte 20 eingreift.In Fig. 2 the area of the control plate 20 is shown enlarged again, the sectional plane with respect the presentation Fig. 1 rotated by 90 °. Identical components are provided with identical reference numerals. The cut now passes through the control plate 20 so that a first control opening 32 and a second control opening 33 can be seen. For correct positioning of the control plate 20 in the radial direction, the centering surface 29, with which the control plate 20 is supported at several points of the outer circumference of the outer bearing ring 7 is used. To secure against rotation serves in the illustrated embodiment, another dowel 34 which is inserted into a bore of the housing cover 8 and engages in a corresponding groove in the control plate 20.

Auf der Hochdruckseite ist an dem äußeren Rand 46 der Steuerplatte 20 eine radiale Erweiterung 35 ausgebildet, um den höheren mechanischen Belastungen auf der Hochdruckseite gerecht zu werden. Der nach außen radial erweiterte Bereich 35 sowie der innere Rand 47 der Steuerplatte 20 an dem die Zentrierfläche 29 ausgebildet ist, ist im Vergleich zu der dichtenden Umgebung 27 bzw. der entgegengesetzt orientierten weiteren dichtenden Umgebung 28 hinsichtlich seiner Dicke reduziert. Da der innere Rand 47 der Steuerplatte 20 sowie die radiale Erweiterung 35 an ihren Oberflächen, die in Richtung der Zylindertrommel 4 bzw. in Richtung des Gehäusedeckels 8 orientiert sind lediglich geringe Anforderungen an die Oberflächengüte stellen, kann in, diesem Bereich eine Nachbearbeitung des Rohteils weitgehend entfallen. Im Bereich der dichtenden Umgebung 27 sowie der entgegengesetzt orientierten weiteren dichtenden Umgebung 28 wird dagegen das Rohteil der Steuerplatte 20 entsprechend nachbearbeitet, wobei eine hohe Oberflächenqualität und Ebenheit beispielsweise durch Läppen erreicht wird.On the high pressure side, a radial extension 35 is formed on the outer edge 46 of the control plate 20 in order to cope with the higher mechanical loads on the high pressure side. The outwardly radially widened region 35 and the inner edge 47 of the control plate 20 on which the centering surface 29 is formed, is reduced in thickness compared to the sealing environment 27 and the oppositely oriented further sealing environment 28. Since the inner edge 47 of the control plate 20 and the radial extension 35 on their surfaces, which are oriented in the direction of the cylinder drum 4 and in the direction of the housing cover 8 only low demands on the surface finish, in this area, a post-processing of the blank largely omitted. In contrast, in the region of the sealing environment 27 and the oppositely oriented further sealing environment 28, the blank of the control plate 20 is reworked accordingly, wherein a high surface quality and flatness is achieved, for example, by lapping.

Ein Beispiel für eine konstruktive Ausführung einer Steuerplatte 20 ist in Fig. 3 dargestellt. Die Steuerplatte 20 weist eine im wesentlichen kreisförmige Geometrie auf. In der Mitte ist in der Steuerplatte 20 eine Durchgangsöffnung 38 ausgebildet, die einen Durchmesser von d1 aufweist. Der innere Rand 47 dieser Durchgangsöffnung 38 bildet die Zentrierfläche 29 aus. Die Durchgangsöffnung 38 ist an einzelnen Ausnehmungen 36.1, 36.2 und 36.3 in radialer Richtung nach innen erweitert. Zwischen den Ausnehmungen 36.1 bis 36.3 bleibt jeweils ein Segment 43.1, 43.2 und 43.3 mit einem Innendurchmesser d1 stehen. Dadurch entstehen als Zentrierfläche 29 drei Teilflächen 29.1, 29.2 und 29.3 an den Segmenten 43.1, 43.2 und 43.3. Die dritte Teilfläche 29.3 ist im bevorzugten Ausführungsbeispiel durch das Einbringen einer Ausnehmung 37 noch einmal unterteilt, so dass die dritte Teilfläche 29.3 aus den beiden mit 29.3' und 29.3" bezeichneten Teilflächen besteht. Entsprechend besteht das dritte Segment 43.3 aus den beiden Teilsegmenten 43.3' und 43.3". Die Ausnehmung 37 ist zur Aufnahme des Paßstifts 34 vorgesehen, so dass die Steueröffnungen 32 bzw. 33.1 bis 33.5 eine definierte Position aufweisen.An example of a structural design of a control plate 20 is shown in FIG Fig. 3 shown. The control plate 20 has a substantially circular Geometry on. In the middle, a passage opening 38 is formed in the control plate 20, which has a diameter of d 1 . The inner edge 47 of this passage opening 38 forms the centering surface 29. The passage opening 38 is extended at individual recesses 36.1, 36.2 and 36.3 in the radial direction inwards. Between the recesses 36.1 to 36.3 in each case a segment 43.1, 43.2 and 43.3 with an inner diameter d 1 remains. As a result, three partial surfaces 29.1, 29.2 and 29.3 are formed on the segments 43.1, 43.2 and 43.3 as the centering surface 29. In the preferred exemplary embodiment, the third subarea 29.3 is subdivided once more by the introduction of a recess 37, so that the third subarea 29.3 consists of the two subareas designated 29.3 'and 29.3 ", correspondingly the third segment 43.3 consists of the two subsegments 43.3' and 43.3 ". The recess 37 is provided for receiving the dowel 34, so that the control openings 32 and 33.1 to 33.5 have a defined position.

Im dargestellten Ausführungsbeispiel sind die Ausnehmungen 36.1, 36.2 und 36.3 gleichmäßig über den Umfang der Durchgangsöffnung 38 verteilt angeordnet. Ihre radiale Erweiterung erstreckt sich bis zu einem Durchmesser d2, welcher groß genug ist, um zu dem äußeren Lagerring 7 den Spalt 22 auszubilden, der von einem Leckagefluid passierbar ist.In the illustrated embodiment, the recesses 36.1, 36.2 and 36.3 are distributed uniformly over the circumference of the passage opening 38. Its radial extension extends to a diameter d 2 , which is large enough to form to the outer bearing ring 7, the gap 22, which is passable by a leakage fluid.

Die Steuerplatte 20 weist weiterhin die nierenförmige Niederdruck-Steueröffnung 32 auf, über welche die Öffnungen 21 der Zylindertrommel 4 mit dem Niederdruckanschluss verbunden werden. Zur Verbindung der Öffnungen 21 mit einem Hochdruckanschluss sind im dargestellten Ausführungsbeispiel mehrere ebenfalls nierenförmige Hochddruck-Steueröffnungen vorgesehen, die mit den Bezugszeichen 33.1 bis 33.5 bezeichnet sind. Die jeweils benachbarten Hochdruck-Steueröffnungen 33.1 bis 33.5 sind durch einen Trennsteg 39.1 bis 39.4 voneinander getrennt. Zwischen den Steueröffnungen 32 und 33.1 bis 33.5 sind Trennflächen 41 und 42 ausgebildet, die bei eingebauter Steuerscheibe 20 im Bereich des oberen und des unteren Totpunkts die Öffnungen 21 verschließen, wie dies in Fig. 1 dargestellt ist.The control plate 20 further includes the kidney-shaped low-pressure control port 32, via which the openings 21 of the cylinder drum 4 are connected to the low pressure port. In order to connect the openings 21 to a high-pressure connection, a plurality of likewise kidney-shaped high-pressure control openings are provided in the embodiment shown, which are designated by the reference numerals 33.1 to 33.5. The respective adjacent high-pressure control openings 33.1 to 33.5 are separated by a separating web 39.1 to 39.4. Between the control openings 32 and 33.1 to 33.5 separating surfaces 41 and 42 are formed, which close the openings 21 with built-in control disk 20 in the region of the top and bottom dead center, as in Fig. 1 is shown.

Während die Ausdehnung der Steuerplatte 20 in radialer Richtung im Bereich der Niederdruck-Steueröffnung 32 lediglich geringfügig größer ist, als die radiale Ausdehnung der Steueröffnung 32 selbst, ist im Bereich der Hochdruck-Steueröffnungen 33.1 bis 33.5 zusätzlich eine radiale Erweiterung 35 ausgebildet. Die radiale Erweiterung 35 weist einen äußeren Rand 40 auf, der kreisbogenförmig verläuft und der konzentrisch zu der kreisscheibenförmigen Geometrie der Steuerplatte 20 ausgebildet ist.While the extent of the control plate 20 in the radial direction in the region of the low-pressure control opening 32 is only slightly greater than the radial extent of the control opening 32 itself, a radial extension 35 is additionally formed in the region of the high-pressure control openings 33.1 to 33.5. The radial extension 35 has an outer edge 40, which extends in a circular arc and which is formed concentrically to the circular disk-shaped geometry of the control plate 20.

Die Steuerplatte 20 wird aus einem Rohteil gefertigt, das vorzugsweise in einem Warmschmiedeprozess hergestellt wird. Das Rohteil ist dabei in dem Bereich der radialen Erweiterung 35 sowie im Bereich zwischen den Durchmessern d1 und d2 von geringerer Dicke als in dem dichtenden Bereich 27 bzw. 28. Das Herausarbeiten der radialen Vergrößerung der Ausnehmungen 36.1, 36.2 und 36.3 erfolgt bereits im Warmschmiedeprozess oder durch spanende Bearbeitung, ebenso wie das Einbringen der Ausnehmung 37 für den weiteren Paßstift 34. Die Steueröffnungen 32 bzw. 33.1 bis 33.5 werden dagegen vorzugsweise gestanzt, wobei das Stanzen im warmen oder im kalten Zustand erfolgen kann. Abschließend werden die dichtenden Umgebungen 27 und 28 beispielsweise durch Läppen bearbeitet.The control plate 20 is made of a blank, which is preferably produced in a hot forging process. The blank is in the region of the radial extension 35 and in the region between the diameters d 1 and d 2 of lesser thickness than in the sealing region 27 and 28. The working out of the radial enlargement of the recesses 36.1, 36.2 and 36.3 already takes place in Hot forging process or by machining, as well as the introduction of the recess 37 for the other dowel 34. The control ports 32 and 33.1 to 33.5, however, are preferably punched, the punching can be done in the warm or cold state. Finally, the sealing environments 27 and 28 are processed by lapping, for example.

In Fig. 4 ist ein Schnitt durch die Steuerplatte 20 entlang der Linie IV - IV in Fig. 3 gezeigt. In der Schnittdarstellung ist noch einmal zu erkennen, dass im Bereich der dichtenden Umgebung 27 sowie der weiteren dichtenden Umgebung 28 der Steueröffnungen 32 und 33 eine größere Dicke t2 der Steuerplatte 20 im Vergleich zu der Dicke t1 im Bereich der radialen Erweiterung 35 und der Zentrierfläche 29 bzw. der Segmente 43.1 bis 43.3 vorgesehen ist, wobei die Dickenänderung vorzugsweise auf beiden Seiten der Steuerplatte 20 erfolgt. Durch die Reduzierung der Dicke in Teilbereichen der Steuerplatte 20 sowie durch die Verringerung des Außendurchmessers der Steuerplatte 20 im Vergleich zu herkömmlichen Steuerplatten ist eine erhebliche Reduzierung des Gesamtgewichts möglich. Außerdem wird durch das Reduzieren der Dicke t1 der Steuerplatte 20 in denjenigen Bereichen, welche keine dichtende Funktion haben, der Anteil an spanender Bearbeitung von etwa 50 % auf etwa 20 % reduziert. Neben der Kostensenkung durch den verringerten Materialeinsatz ergibt sich als weiterer Vorteil eine Verkürzung der Bearbeitungszeit.In Fig. 4 is a section through the control plate 20 along the line IV - IV in Fig. 3 shown. In the sectional view can be seen again that in the area of the sealing environment 27 and the other sealing environment 28 of the control openings 32 and 33 has a greater thickness t 2 of the control plate 20 compared to the thickness t 1 in the region of the radial extension 35 and Centering surface 29 and the segments 43.1 to 43.3 is provided, wherein the thickness change preferably takes place on both sides of the control plate 20. By reducing the thickness in portions of the control plate 20 and by reducing the outer diameter of the control plate 20 compared to conventional control plates, a significant reduction of the total weight is possible. In addition, by reducing the thickness t 1 of the control plate 20 in those areas which have no sealing function, the proportion of machining reduces from about 50% to about 20%. In addition to the cost reduction due to the reduced use of materials, a further advantage is a shortening of the processing time.

Claims (13)

  1. Control plate for an axial piston engine having at least two control openings (32, 33, 33.1 - 33.5), by means of which cylinder bores (9) of a cylinder drum (4) mounted rotatably in a housing (2) are connected upon rotation of the cylinder drum (4) alternately to a high-pressure port (26) and a low-pressure port (26'), wherein in the control plate (20) a through-opening (38) is formed,
    characterized in
    that the radially inner edge (47) of the control plate (20) takes the form of a centring surface (29) that centres the control plate (20) on a housing-side centring body (7) and
    that the centring surface (29) comprises a plurality of sub-surfaces (29.1, 29.2, 29.3), which are formed on segments (43.1, 43.2, 43.3) of the inner edge (47) of the control plate (20) that extend radially inwards into the through-opening (38) and are separated by recesses (36.1, 36.2, 36.3).
  2. Control plate according to claim 1,
    characterized in
    that the centring surface (29) comprises three sub-surfaces (29.1, 29.2, 29.3) that are distributed over the circumference of the inner edge (47) of the control plate (20).
  3. Control plate according to one of claims 1 to 2,
    characterized in
    that the at least two control openings (32, 33, 33.1 - 33.5) comprise high-pressure control openings (33.1 - 33.5) and a low-pressure control opening (32) and that at an outer edge (46) of the control plate (20) in the region of the high-pressure control openings (33.1 - 33.5) an outer radial widening (35) of the control plate (20) is formed.
  4. Control plate according to one of claims 1 to 3,
    characterized in
    that on the centring surface (29) a further recess (37) for receiving an anti-rotation element (34) is provided.
  5. Control plate according to one of claims 1 to 4,
    characterized in
    that the thickness (t1) of the control plate (20) in the region of the centring surface (29) and/or the radial widening (35) is reduced compared to the thickness (t2) of a sealing environment (27, 28) of the control openings (32, 33, 33.1 - 33.5).
  6. Control plate according to claim 5,
    characterized in
    that the sealing environment (27) of the control openings (32, 33, 33.1 - 33.5) is of a spherical configuration.
  7. Control plate according to one of claims 1 to 6,
    characterized in
    that the segments (43.1, 43.2, 43.3) extend over a smaller angle than the recesses (36.1, 36.2, 36.3) situated between them.
  8. Axial piston engine comprising a cylinder drum (4), which is mounted rotatably in a housing and into which are introduced cylinder bores (9), in which pistons (10) are disposed in an axially displaceable manner, wherein the cylinder bores (9) have in the direction of an end face (19) of the cylinder drum (4) openings (21), which during a rotation of the cylinder drum (4) are connected by at least two control openings (32, 33, 33.1 - 33.5) of a control plate (20) alternately to a high-pressure port (26) and a low-pressure port (26'),
    characterized in
    that the control plate (20) is configured according to one of claims 1 to 7.
  9. Axial piston engine according to claim 8,
    characterized in
    that the cylinder drum (4) is disposed in a rotationally fixed manner on a shaft (3), wherein the shaft (3) is mounted at the control plate (20) end in the housing (8) and the control plate (20) is centred by the centring surface (29) on an outer bearing ring (7) of a rolling-contact bearing (6).
  10. Axial piston engine according to one of claims 8 to 9,
    characterized in
    that in order to form a leakage path the radial extent (d2) of the individual recesses (36.1, 36.2, 36.3) of the inner edge (47) of the control plate (20) is greater than the radial extent of the centring body (7).
  11. Axial piston engine according to one of claims 8 to 10,
    characterized in
    that at an outer edge (46) of the control plate (20) in the region of the at least one control opening (33, 33.1 - 33.5) connected to the high-pressure port an outer radial widening (35) of the control plate (20) is formed.
  12. Axial piston engine according to one of claims 8 to 11,
    characterized in
    that on the side of the control plate (20) remote from the cylinder drum (4) there is provided in the region of a separating surface (41, 42) at least one slot (25), which extends from at least one recess (36.1, 36.2, 36.3) of the inner edge (46) of the control plate (20) to the outer edge (46) of the control plate (20) and which connects an inner leakage volume (44) to an outer leakage volume (45).
  13. Axial piston engine according to one of claims 8 to 12,
    characterized in
    that the end face (29) of the cylinder drum (4) and a sealing environment (27) of the control plate (20) that is adjacent thereto are of a spherical configuration.
EP03788997A 2002-11-05 2003-11-03 Axial piston engine and a control plate for an axial piston engine Expired - Fee Related EP1590569B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10251552A DE10251552C5 (en) 2002-11-05 2002-11-05 Axial piston machine and control plate for an axial piston machine
DE10251552 2002-11-05
PCT/EP2003/012248 WO2004042229A1 (en) 2002-11-05 2003-11-03 Axial piston engine and a control plate for an axial piston engine

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EP1590569A1 EP1590569A1 (en) 2005-11-02
EP1590569B1 true EP1590569B1 (en) 2012-01-18

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US (1) US7661937B2 (en)
EP (1) EP1590569B1 (en)
DE (1) DE10251552C5 (en)
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DE102021212096A1 (en) 2021-10-27 2023-04-27 Robert Bosch Gesellschaft mit beschränkter Haftung Control plate for an axial piston machine, and axial piston machine with a control plate

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DE10251552B3 (en) 2004-07-15
US20060169072A1 (en) 2006-08-03
DE10251552C5 (en) 2010-07-15
WO2004042229A1 (en) 2004-05-21
EP1590569A1 (en) 2005-11-02
US7661937B2 (en) 2010-02-16

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