GB2545878A

GB2545878A - A hydraulic axial piston machine

Info

Publication number: GB2545878A
Application number: GB1516311.6A
Authority: GB
Inventors: Kuehne Manfred
Original assignee: Eaton Industrial IP GmbH and Co KG
Current assignee: Eaton Industrial IP GmbH and Co KG
Priority date: 2015-09-15
Filing date: 2015-09-15
Publication date: 2017-07-05
Anticipated expiration: 2035-09-15
Also published as: GB201516311D0; GB2545878B

Abstract

Disclosed is a hydraulic piston machine comprising a housing 1, a cylinder barrel 7 rotatably supported within the housing about a longitudinal axis L and having a central control bore 4, a plurality of cylinder bores 9 in the cylinder barrel arranged parallel to the longitudinal axis, pistons 10, 11 slidably disposed in the cylinder bores and delimiting compression chambers 12, an actuation mechanism 53, 54 reciprocating the pistons in response to rotation of the cylinder barrel, a control element 18, for conveying hydraulic fluid between supply ducts 28, 29 within the housing and the compression chambers, arranged within the control bore and supported non-rotatably relative to the housing, and a cross guide element 25, with transfer holes 26, 27 for transferring hydraulic fluid between the control element and the supply ducts, slidably supported against the housing in a first radial direction. The control element is slidably supported against the cross guide element in a second radial direction different to the first radial direction. The arrangement compensates for radial displacement between the control element and the housing in two directions.

Description

A hydraulic axial piston machine

Description

The invention relates to a hydraulic piston machine comprising a housing rotably supporting a cylinder barrel about a longitudinal axis. The cylinder barrel has a central control bore and a plurality of cylinder bores which are arranged parallel to the longitudinal axis. Pistons are slidably disposed in the cylinder bores and delimit compression chambers within the cylinder bores. An actuation mechanism drives the pistons within the cylinder bores in a reciprocating manner in response to a rotation of the cylinder barrel about the longitudinal axis. A control pin is arranged in the control bore of the cylinder barrel and is supported non-rotatably relative to said housing wherein the control pin conveys hydraulic fluid between supply ducts within the housing and the compression chambers.

Such a hydraulic piston machine is known from US 2011/0243780 A1 which discloses an axial piston pump or motor wherein in each cylinder bore two pistons are arranged which are driven in opposite directions and which together delimit the compression chambers.

Such axial piston machines can be used as a motor or as a pump. In motor operation, hydrostatic energy is converted into mechanical energy. Pressurized fluid is conveyed to the pressure chambers so that the cylinder barrel is driven in a rotational manner so that mechanical energy can be outputted for example from an output shaft which is coupled to the cylinder barrel. In pump operation mechanical energy of the rotation of the cylinder barrel is converted into hydrostatic energy. The mechanical energy can be provided by driving an input shaft which is connected to the cylinder barrel.

In the axial piston machine according to US 2011/0243780 A1 the cylinder bores are arranged parallel to the longitudinal axis and each two displacement pistons of each cylinder chamber are displaceable within the respective cylinder bore parallel to the longitudinal axis and in opposite directions to one another. The pistons are moved simultaneously towards one another and away from one another and, in this way, can cause a large change in volume of the compression chamber within a comparative small stroke.

For the reciprocating movement of the pistons the pistons protrude from the cylinder barrel out of the cylinder bores. The pistons of each pair of pistons protrude from opposite ends of the cylinder barrel. The pistons are supported against a cam surface of a swash plate. The cam surface defines a plane arranged transverse to the longitudinal axis and can be adjusted. If the cam surface is arranged perpendicular to the longitudinal axis of the pistons, which are held in contact against the cam surface, the pistons do not move within the cylinder bores upon rotation of the cylinder barrel. As soon as the cam angle between the cam surface and the longitudinal axis is changed to an angle different to the perpendicular orientation of the cam surface to the longitudinal axis the pistons are moving within the cylinder bores upon a rotation of the cylinder barrel. This causes, hence, a reciprocating variation of the volume of the compression chambers so that, in pump operation, hydraulic fluid can be pumped and in motor operation the cylinder barrel can be driven.

To achieve this movement of the pistons it is essential that the pistons are always axially supported against the cam surface. This can be done by a hold-down disc which holds protruding ends of the pistons against the cam surface. Another option is to bias the pistons against the cam surface by a pressure spring.

The cam surface is part of the swash plate, which is adjustable, or of a wedge plate which has a fixed angle relative to the longitudinal axis.

The compression chambers each have openings for conveying hydraulic fluid into or out of the compression chamber via hydraulic ducts within the housing to hydraulic ports of the axial piston machine. The openings of the cylinder bores are arranged transversely to the longitudinal axis and run from the compression chamber to channels of a control element. The control element is either arranged within a central bore of the cylinder barrel or part of the housing and arrange in form of a tube around the cylinder barrel wherein the control element is held non-rotatably relative to the housing so that the cylinder barrel rotates relative to the control element. The control element has two different channels, an inlet channel and outlet channel. The channels are connected to hydraulic ducts within the housing which lead to hydraulic ports, wherein the inlet channel is connected to an inlet duct leading to an inlet port and the outlet channel is connected to an outlet duct leading to an outlet port. In motor operation high pressure hydraulic fluid is conveyed from the inlet port through the inlet duct into the inlet channel of the control element into the compression chambers for moving the pistons away from each other and rotating the cylinder barrel. After expansion of the compression chamber the low pressure hydraulic fluid is discharged through the openings, the outlet channel of the control element, the outlet duct and the outlet port out of the axial piston machine. In pump operation the hydraulic fluid path is vice versa.

The control element is arranged within the central bore of the cylinder barrel in a fluid tight manner and the openings of the compression chambers are communicating with openings of the hydraulic channels of the control element. The inlet channel and the outlet channel are arranged on opposite sides of the hydraulic piston machine and can be connected to ducts of the hydraulic piston machine. US 5 081 908 A describes a similar hydraulic piston machine. Each cylinder bore accommodates one piston. The control element is arranged within a central bore. The hydraulic channels of the control element communicate with hydraulic ducts within the housing. In order to compensate radial displacements of the cylinder barrel relative to the longitudinal axis and, hence, to compensate the same radial movement of the control element relative to the housing the control elements sits within a bore of the housing with radial clearance. In order to convey hydraulic fluid from the hydraulic channels of the control element to the hydraulic ducts of the housing, tubes are provided within the hydraulic channels and protruding into the hydraulic ducts wherein the tubes are sealed on an outside surface against the hydraulic channel and the hydraulic duct so that hydraulic fluid can be conveyed between the hydraulic channel through the tubes and the hydraulic ducts. If a radial displacement occurs the tubes, which have a radial clearance within the hydraulic channel and the hydraulic duct, can tilt relative to an axis parallel to the longitudinal axis compensating radial dis- placement of the cylinder barrel relative to the housing.

In order to avoid a rotation of the control element relative to the housing about the longitudinal axis the control element has radially projecting pins which are arranged within radially orientated pockets in the housing enabling a radial movement of the control element in all directions and providing a support against rotational movement.

However, due to the fact that in order to provide radial movement of the control element in all directions the pins are arranged within the pockets within clearance in radial direction and circumferential direction so that a limited rotation of the control element about the longitudinal axis is still possible.

Object of the invention is to provide a hydraulic piston machine, having a control element which compensates radial displacements avoiding rotational movement as much as possible.

The object is achieved by a hydraulic piston machine comprising a housing, a cylinder barrel rotatably supported within said housing about a longitudinal axis and having a central control bore, a plurality of cylinder bores in said cylinder barrel arranged parallel to said longitudinal axis, pistons slidably disposed in said cylinder bores and delimiting compression chambers within said cylinder bores, an actuation mechanism reciprocating said pistons in said cylinder bores in response to a rotation of said cylinder barrel about the longitudinal axis, a control element for conveying hydraulic fluid between supply ducts within the housing and said compression chambers, wherein the control element is arranged within said control bore and is supported non-rotatably relative to said housing, and a cross guide element with transfer holes for transferring hydraulic fluid between the control element and said supply ducts, wherein said cross guide element is slidably supported against the housing in a first radial direction and wherein said control element is slidably supported against said cross guide element in a second radial direction different to the first radial direction.

According to the invention the control element is supported against the housing indirectly via the cross guide element. The cross guide element is supported on one hand against the housing and on the other hand against the control element. The cross guide element can be supported against the housing and/or against the control pin directly or, alternatively, indirectly via further parts which are fixed to the housing or the control element, respectively. Hence, the cross guide element would comprise three single parts so that all features for radial compensation can be provided in the cross guide element and the housing and the control element do not have to be manufactured in a special way.

The advantage of the cross guide element compared to solutions according to the prior art is that the cross guide element is compensating radial displacements between the control element and the housing in a first direction between the cross guide element and the housing and in a second radial direction, which is different to the first radial direction, between the cross guide and the control element. Hence, the compensation in two different radial directions are separated from each other. It is, therefore, possible to provide a sliding guide for each radial direction, having a very small clearance transverse to the respective radial direction. In the first radial direction the cross guide element is only able to slide in the first radial direction with a very small clearance in a direction transverse to the first direction. Relative to the control element a cross guide element only allows a sliding movement in the second radial direction with a very small clearance in a direction transverse to the second radial direction. Therefore, when compensating a radial displacement of the cylinder barrel relative to the housing the cross guide element does not make any substantial rational movement.

In particular, the first radial direction is orientated perpendicular to the second radial direction.

In a preferred embodiment the cross guide element has a first side facing the hous- ing with two oppositely arranged first guide surfaces extending parallel to the first radial direction and the first guide surfaces are supported against corresponding first support surfaces of the housing in the second radial direction. Alternatively, the first support surfaces of the housing can be part of a separate control guide part which is fixed to the housing.

The first guide surfaces can be part of a first radial recess so that the first guide surfaces are facing each other.

The transfer holes, preferably, open into the first radial recess.

In a preferred embodiment the cross guide element has a second side facing the control element with two oppositely arranged second guide surfaces extending parallel to the second radial direction and wherein the second guide surfaces are supported against corresponding second support surfaces of the control element in the second radial direction. Alternatively, the second support surfaces can be part of a separate cross guide part which is fixed to the control element.

Preferably, the second guide surfaces are part of a second radial recess wherein the second guide surfaces are facing each other.

The transfer holes preferably open into the second radial recess.

According to a preferred embodiment the cylinder barrel is rotatably supported with said housing via a plain bearing. Plain bearings are hydrodynamic bearings so that in a stopped condition without rotation of the cylinder barrel, the cylinder barrel is moved downwardly in a vertical direction. During rotation of the cylinder barrel the cylinder barrel is lifted upwardly due to hydrodynamic pressure so that a radial clearance between the cylinder barrel and the housing increases in the area below the cylinder barrel. This radial displacement of the cylinder barrel has to be compensated by the cross guide element.

In order to provide a fast hydrodynamic effect when starting the rotation of the cylin- der barrel hydraulic pressure ducts can be provided in the housing which convey pressurized hydraulic fluid from a hydraulic source to the plain bearing so that the cylinder barrel is centred within the housing before the rotation of the cylinder barrel starts.

Preferably, the hydraulic piston machine is a hydraulic axial piston machine, in particular, a hydraulic axial piston motor or pump. In each cylinder bore two oppositely arranged pistons can be accommodated which are moved towards or away from each other in a reciprocating way.

The hydraulic axial piston machine may further comprise a drive shaft which is connected to the cylinder barrel and which is supported in the housing via a spherical plain bearing. This spherical plain bearing provides for compensation of a deformation of the drive shaft due to high external forces acting onto the drive shaft. The spherical plain bearing can also be connected to hydraulic high pressure ducts comparable to the plain bearing of the cylinder barrel within the housing.

Preferably, the actuation mechanism comprises a wedge plate cooperating with the pistons wherein the cross guide element is secured to the housing by said wedge plate.

Advantages, features in details of the invention will become apparent from the drawings which show one preferred embodiment of the inventive hydraulic piston machine.

Figure 1 is a longitudinal sectional view of a hydraulic piston machine;

Figure 2 is an enlarged view of the detail X of Fig. 1;

Figure 3 is a perspective view of a centre tube of the housing of the hydraulic piston machine according to Fig. 1;

Figure 4 is a perspective view of the cylinder barrel of the hydraulic piston machine according to Fig. 1;

Figure 5 is a perspective view of a control element of the hydraulic piston machine according to Fig. 1;

Figure 6 is a perspective view of a drive head of the housing of the hydraulic piston machine according to Fig. 1;

Figure 7 is a first perspective view of the cross guide element of the hydraulic piston machine according to Fig. 1;

Figure 8 is a second perspective sectional view of the cross guide element according to Fig. 7; and

Figure 9 is a perspective view of a compensation tube.

Figures 1 to 9 depict the hydraulic piston machine according to the invention in different views and different parts thereof. The Figures are, in the following, described together.

As can be taken from Figures 1 and 2 the hydraulic piston machine comprises a housing 1 which has a centre tube 2 coaxially arranged to a longitudinal axis L. At one axial end the centre tube 2 is connected to a drive head 3. The drive head 3 is, as explained later, provided with hydraulic ports for supplying hydraulic fluid to the hydraulic piston machine. The drive head 3 is closed by a cover 5.

At the other end, which is opposed to the drive head 3, the centre tube 2 is connected to a bearing head 4. The bearing head 4 supports a drive shaft 15.

The centre tube 2 is provided with an inner bearing bore 6 (Fig. 3). The bearing bore 6 accommodates a cylinder barrel 7 which has an outer bearing surface 8. The bearing bore 6 and the outer bearing surface 8 together constitute a plain bearing for rota-tionally supporting the cylinder barrel 7 within the centre tube 2 so that the cylinder barrel 7 can rotate about the longitudinal axis L within the centre tube 2. The plain bearing further comprises two bearing bushings 59, 59’ between the bearing bore 6 and the outer bearing surface 8.

The cylinder barrel 7 is provided with a plurality of cylinder bores 9 which are arranged parallel to the longitudinal axis and which are evenly distributed in a circumferential direction. The cylinder bores 9 run from a first end 16 of the cylinder barrel 7 to a second end 17 of the cylinder barrel 7.

In each cylinder bore 9 two pistons 10, 11 are arranged. The pistons are slideably disposed in the respective cylinder bore and delimit a compression chamber 12 between each other.

Each compression chamber 12 is in fluid contact with an inlet/outlet opening 13 within the cylinder barrel 7. Each opening 13 leads to a central control bore 14 within the cylinder barrel 7. The central control bore 14 is arranged coaxial to the longitudinal axis L and is open towards the first end 16 of the cylinder barrel 7. The control bore 14 accommodates a control element 18 which projects out of the control bore 14 at the first end 16 of the cylinder barrel 7. The control element 18 has an annular sealing face 19 (Fig. 5) which is in sealing contact with the inner surface of the control bore 14. Opposite to the sealing face 19 the control element 18 is provided with a flange portion 20. Starting from a front face 32 of the flange portion 20 an outlet channel 21 and an inlet channel 22 are provided within the control element 18. Both channels 21,22 are arranged parallel to the longitudinal axis L and lead to two outlet openings 23 (one of which is disclosed in Fig. 5) and to two inlet openings 24, 24’, respectively. The openings 23, 24, 24’ are arranged within the sealing face 19 and communicate with the inlet/outlet openings 13 of the cylinder barrel 7.

The control element 18 is supported in a non-rotatably manner relative to the drive head 3 of the housing 1 via a cross guide element 25 which is arranged between the control element 18 and the drive head 3. The cross guide element 25 has a first transfer hole 26 and a second transfer hole 27 (Fig. 7, Fig. 8) which are formed as through-holes through the cross guide element 25. The first transfer hole 26 is arranged coaxially to the low pressure channel 21 and the second transfer hole 27 is coaxially to the high pressure channel 22.

The first transfer hole 26 further is coaxially arranged to an outlet duct 28 within the drive head 23. The second transfer hole 27 is arranged coaxially to an inlet duct 29 of the drive head 3. The outlet duct 28 conveys hydraulic fluid to an outlet port 30 which can be seen in Fig. 6. The inlet duct 29 leads to an inlet port 31 of the drive head 3.

Figure 7 and 8 show the cross guide element 25 in different perspective views and more detail. The cross guide element 25 has a first side 33 which is in contact to the drive head 3 of the housing 1. Further, the cross guide element 25 has a second side 34 which is held in contact to the control element 18.

At the first side 33 the cross guide element 25 has a first radial recess 35 which extends in a first radial direction relative to the longitudinal axis L. At the second side 34 the cross guide element 25 is provided with a second radial recess 36 extending in a se-cond radial direction relative to the longitudinal axis L. In the depicted preferred embodiment the first radial direction is orientated perpendicular to the second radial direction when viewed onto the cross guide element 25 in the direction of the longitudinal axis L.

The first radial recess 35 forms two opposing first guide surfaces 37, 37’ which are facing each other. The second radial recess 36 forms oppositely arranged second guide surfaces 38, 38’ which face each other.

As can best be seen in Fig. 6 the drive head 3 is provided with a first protrusion 39 protruding in a direction of the longitudinal axis L. The first protrusion 39 has two oppositely arranged first support surfaces 40, 40’ which are facing away from each other. The first support surfaces 40, 40’ extend in a direction parallel to a first radial direction relative to the longitudinal axis L. The distance between the first support surfaces 40, 40’ is substantially equal to the distance between the first guide surfaces 37, 37’. The cross guide element 25 is in contact to the drive head 3 such that each first guide surface 37, 37’ is in supporting contact to one of the first support surfaces 40, 40’. Hence, the cross guide element 25 is slideably supported on the first protrusion 39, wherein the cross guide element 25 can be moved along the first support surfaces 40, 40’ in the first radial direction.

As can best be seen from Fig. 5 the control element 18 is provided with a second protrusion 41 on the front face 32. The second protrusion 41 forms two second support surfaces 42, 42’ which are arranged oppositely and facing away from each other. The second support surfaces 42, 42’ extend parallel to the second radial direction. The cross guide element 25 is in contact to the control element 18 such that each second guide surface 38, 38’ is in supporting contact to one of the second support surfaces 42, 42’. Hence, the cross guide element 25 is slideably supported on the second protrusion 41, wherein the cross guide element 25 can be moved along the second support surfaces 42, 42’ in the second radial direction.

Consequently, the first radial recess 35 of the cross guide element 25 and the first protrusion 39 of the drive head 3 enable the control element 18 to be displaced in the first radial direction. The second radial recess 36 of the cross guide element 25 and the second protrusion 41 of the control element 18 enable a displacement of the control element 18 in the second radial direction. Due to very small tolerances between the protrusions 39, 41 and the radial recesses 35, 36 it is avoided that the control element 18 can be rotated about the longitudinal axis wherein a displacement in any radial direction is possible.

Fig. 2 discloses an enlarged sectional view of the area X of Fig. 1 of the outlet channel 21, the outlet duct 28 and the cross guide element 25. As can be seen in Fig. 1 in each of the inlet and outlet channels 21, 22 sits a compensation tube 43, 44. The compensation tube 43 in the inlet channel 22 of the control element 18 is disclosed in detail with reference to Fig. 2 and also representing the features of the compensation tube 44 in the outlet channel 21. The compensation tube 43 is also disclosed in a perspective view in Fig. 9 and is identical to the compensation tube 44 in the outlet channel 21.

The compensation tube 43 has a first end 45 and a second end 46 and can convey hydraulic fluid between the first end 45 and the second end 46. The first end 45 sits within inlet duct 29 of the drive head 3. The compensation tube 43 projects out of the inlet duct 29 towards the inlet channel 22 and sits within the inlet channel 22 with its second end 46 wherein the compensation tube 43 reaches through the second transfer hole 27 of the cross guide element 25.

At the first end 45 the compensation tube 43 has an annular first bead 47 on an outer circumference. At the second end 46 the compensation tube 43 is provided with an annular second bead 48 on the outer circumference. Each of the beads 47, 48 is provided with a groove 49, 50 for accommodating a sealing O-ring 51,52 so that the compensation tube 43 is sealed against the inlet duct 29 and the inlet channel 22 for conveying fluid between the inlet duct 29 and the inlet channel 22 through the compensation tube 43.

Due to the fact, that the compensation tube 43 sits within the inlet duct 29 and the inlet channel 22 with its first and second beads 47, 48 there is a radial clearance between the outer circumference of the compensation tube 43 in other regions than in the regions of the beads 47, 48 to the inlet duct 29 and the inlet channel 22 as well as to the inner circumference of the second transfer hole 27. Therefore, if a radial displacement between the control element 18 and the drive head 3 of the housing 1 occurs the compensation tube 43 can tilt in a radial direction relative to the drive head 3 and the control element 18. Even, if the compensation tube 43 is tilted within the inlet duct 29 and the inlet channel 22 the sealing connection between the compensation tube 43 and the inner surfaces of the inlet duct 29 and the inlet channel 22 is still maintained by the O-rings 51.

In the following the actuation mechanism for reciprocating the pistons 10, 11 is described, wherein the actuation mechanism for reciprocating the pistons 10 on the left side, shown in Fig. 1, is identical to the actuation mechanism for reciprocating the pistons 11 on the right side of Fig. 1 so that in the following the actuation mechanism for the pistons 10 on the left side is described. The actuation mechanism can best be seen in Figs. 1 and 2. Each of the pistons 10 is pivotally connected to a piston shoe 54 by a ball joint (Fig. 2). Each piston 10 is connected to the piston shoe 54 at an end which projects out of the cylinder barrel 7. The piston shoe 54 is held in sliding contact to a cam surface 55 of a wedge plate 53.

The cam surface 55 defines a plane transverse to the longitudinal axis L and tilted to the longitudinal axis L. This means, that the plane of the bearing surface 55 is not orientated perpendicular to the longitudinal axis. The pistons 10 are biased by spring elements 56 between each pair of pistons 10 and 11 in each cylinder bore 9 in the direction towards the wedge plate 53. Hence, the piston shoe 54 is held in sliding contact to the cam surface 55. Consequently, upon rotation of the cylinder barrel 7 the piston 10 is moved reciprocatingly within the respective cylinder bore 9.

The wedge plate 53 is fixed to the drive head 3 and is provided with an annular flange portion 57 projecting radially inwardly. The flange portion 57 forms a holding face 58 which faces towards the drive head 3 and supports and holds the flange portion 20 and the cross guide element 25 against the drive head 3 in an axial direction.

The cylinder barrel 7 is connected via a spline connection 60 to the drive shaft 15 which can rotate together with the cylinder barrel 7 about the longitudinal axis L. The drive shaft 15 is supported within the bearing head 4 by a plain bearing which comprises an inner bearing ring 61 and an outer bearing ring 62. The inner bearing ring 61 is non-rotatably connected to the drive shaft 15. The outer bearing ring 62 is non-rotatably connected to the bearing head 4. The inner bearing ring 61 has an outer spherical face 64 which is in sliding contact to an inner spherical face 63 of the outer bearing ring 62. The spherical faces 63, 64 allow a compensation of a deflection of the drive shaft 15 due to high outer forces acting onto the drive shaft 15. These deflections and displacements of the drive shaft 15 also are transferred onto the cylinder barrel 7 so that this may cause a radial displacement of the cylinder barrel 7 which can be compensated by the cross guide element 25.

Reference numerals list 1 housing 2 centre tube 3 drive head 4 bearing head 5 cover 6 bearing bore 7 cylinder barrel 8 outer bearing surface 9 cylinder bore 10 piston 11 piston 12 compression chamber 13 inlet/outlet opening 14 control bore 15 drive shaft 16 first end 17 second end 18 control element 19 sealing face 20 flange portion 21 outlet channel 22 inlet channel 23 outlet opening 24 inlet opening 25 cross guide element 26 first transfer hole 27 second transfer hole 28 outlet duct (supply duct) 29 inlet duct (supply duct) 30 outlet port 31 inlet port 32 front face 33 first side 34 second side 35 first radial recess 36 second radial recess 37, 37’ first guide surface 38, 38’ second guide surface 39 first protrusion 40, 40’ first support surface 41 second protrusion 42, 42’ second support surface 43 compensation tube 44 compensation tube 45 first end 46 second end 47 first bead 48 second bead 49 groove 50 groove 51 O-ring 52 O-ring 53 wedge plate 54 piston shoe 55 bearing surface 56 spring element 57 flange portion 58 holding face 59, 59’ bearing bushing 60 spline connection 61 inner bearing ring 62 outer bearing ring 63 inner spherical face 64 outer spherical face L longitudinal axis

Claims

1. A hydraulic piston machine comprising: a housing (1), a cylinder barrel (7) rotatably supported within said housing (1) about a longitudinal axis (L) and having a central control bore (4), a plurality of cylinder bores (9) in said cylinder barrel (7) arranged parallel to said longitudinal axis (L), pistons (10, 11) slidably disposed in said cylinder bores (9) and delimiting compression chambers (12) within said cylinder bores (9), an actuation mechanism (53, 54) reciprocating said pistons (10, 11) in said cylinder bores (9) in response to a rotation of said cylinder barrel (7) about the longitudinal axis (L), a control element (18) for conveying hydraulic fluid between supply ducts (28, 29) within the housing (1) and said compression chambers (12), wherein the control element (18) is arranged within said control bore (14) and is supported non-rotatably relative to said housing (1), and a cross guide element (25) with transfer holes (26, 27) for transferring hydraulic fluid between the control element (18) and said supply ducts (28, 29), wherein said cross guide element (25) is slidably supported against the housing (1) in a first radial direction and wherein said control element (18) is slidably supported against said cross guide element (25) in a second radial direction different to the first radial direction.

2. The hydraulic axial piston machine according to any one of the preceding claims, wherein the hydraulic piston machine is a hydraulic axial piston machine, in particular a hydraulic axial piston motor.

3. The hydraulic axial piston machine according to any one of the preceding claims, wherein each cylinder bore (9) accommodates two oppositely arranged pistons (10, 11).

4. The hydraulic axial piston machine according to claim 1, wherein the cross guide element (25) has a first side (33) facing the housing (1) and having two oppositely arranged first guide surfaces (37, 37’) extending parallel to the first radial direction and wherein the first guide surfaces (37, 37’) are supported against corresponding first support surfaces (40, 40’) of the housing (1) in the second radial direction.

5. The hydraulic axial piston machine according to claim 2, wherein the first guide surfaces (37, 37’) are part of a first radial recess (35).

6. The hydraulic axial piston machine according to claim 3, wherein the transfer holes (26, 27) open into the first radial recess (35).

7. The hydraulic axial piston machine according to any one of the preceding claims, wherein the cross guide element (25) has a second side (34) facing the control element (18) and having two oppositely arranged second guide surfaces (38, 38’) extending parallel to the second radial direction and wherein the second guide surfaces (38, 38’) are supported against corresponding second support surfaces (42, 42’) of the control element in the second radial direction.

8. The hydraulic axial piston machine according to claim 5, wherein the second guide surfaces (38, 38’) are part of a second radial recess (36).

9. The hydraulic axial piston machine according to claim 6, wherein the transfer holes (26, 27) open into the second radial recess (36).

10. The hydraulic axial piston machine according to any one of the preceding claims, wherein each supply duct (28, 29) accommodates a compensation tube (43, 44) which projects out of the supply duct (28, 29) through one of the transfer holes (26, 27) of the cross guide element (25) into a hydraulic channel (21,22) of the control element (18).

11. The hydraulic axial piston machine according to any one of the preceding claims, wherein the cylinder barrel (7) is rotatably supported within said housing (1) via a plain bearing.

12. The hydraulic axial piston machine according to any one of the preceding claims, wherein the hydraulic axial piston machine further comprises a drive shaft (15) which is connected to the cylinder barrel (7) and which is supported in the housing (1) via a spherical plain bearing (61, 62).

13. The hydraulic axial piston machine according to any one of the preceding claims, wherein the actuation mechanism comprises a wedge plate (53) cooperating with the pistons (10) and wherein the cross guide element (25) is secured to the housing (1) by said wedge plate (53).