Hydrostatic Axial Piston Machine

Abstract

A hydrostatic axial piston machine includes a drive shaft and a plurality of cylinder sleeves in which a spherical or ball-shaped section and a spherical or ball-shaped piston are inserted to delimit a respective displacer chamber. The sections are secured on a rotor, while the pistons are secured on a piston disk or piston drum. The piston disk is configured to be tilted at different pivoting angles relative to the rotor in a variable-displacement machine, or the piston disk is tilted continuously relative to the rotor in a constant-displacement machine. The rotor and the piston disk are coupled to one another for conjoint rotation by a driving device. The rotor and the piston disk can also be coupled indirectly by a drive shaft of the machine. A sliding joint axial with respect to a drive shaft is arranged between the rotor and the piston disk.

Description

This application claims priority under 35 U.S.C. §119 to patent application no. DE 10 2013 222 602.0, filed on Nov. 7, 2013 in Germany, the disclosure of which is incorporated herein by reference in its entirety.

BACKGROUND

The disclosure relates to a hydrostatic axial piston machine.

The known types of hydrostatic axial piston machines include not only the classic type of machine with an integral rotating cylinder drum but also a type of machine in which the cylinders are arranged in revolving cylinder sleeves. The different displacer chambers are therefore formed in individual cylinder sleeves, which are articulated on a common rotor via respective ball joints, on the one hand, and into which respective spherical or ball-shaped pistons are inserted, on the other hand, said pistons being secured on a common piston disk. By setting the piston disk obliquely to the rotor or setting the rotor obliquely to the piston disk, the desired stroke motion of the pistons in the cylinder sleeves is produced as the cylinder sleeves revolve with the rotor and with the piston disk. In this case, the rotor or the piston disk is secured on a drive shaft or is formed integrally therewith, wherein the drive shaft serves as an output shaft in the case of an axial piston motor and as an input shaft in the case of an axial piston pump. Axial piston machines of this kind require a driving device in order to synchronize the rotary motion of the rotor and of the piston disk despite the fact of their being set obliquely to one another.

Printed publication DE 10 2007 011 441 A1 discloses a double hydrostatic axial piston machine having two groups of individual cylinder sleeves, in which toothing, a torsionally stiff bellows and a constant velocity rolling bearing clutch are shown as a driving device.

Printed publication DE 10 2012 222 850 A1 shows a hydrostatic axial piston machine with individual cylinder sleeves, wherein a driving pin inserted transversely into the drive shaft is proposed as a driving device, said pin engaging in slots in a collar on an obliquely set rotor disk. A Cardan joint and a constant velocity joint are furthermore proposed as a driving device.

In DE 10 2012 222 743 A1, a hydrostatic axial piston machine is disclosed with individual cylinder sleeves, the obliquely set cylinder end of which is articulated by means of a Cardan joint on the drive shaft.

The disadvantage with hydrostatic axial piston machines of this kind is that there is a rigid coupling between the rotor and the piston disk in the direction of the drive shaft, and therefore these components cannot be pushed apart by a mechanical force (e.g. by a preloading spring).

Given this situation, it is the underlying object of the disclosure to provide a hydrostatic axial piston machine having individual cylinder sleeves, in which this disadvantage is eliminated.

SUMMARY

The object is achieved by a hydrostatic axial piston machine having the features of the disclosure.

The hydrostatic axial piston machine has a drive shaft and a plurality of cylinder sleeves, in which a spherical or ball-shaped section, on the one hand, and a spherical or ball-shaped piston, on the other hand, are inserted in order to delimit a respective displacer chamber. The sections are secured on a rotor, while the pistons are secured on a piston disk or piston drum. Depending on the embodiment, the piston disk and the rotor can be tilted relative to one another in a variable-displacement machine, or the piston disk and the rotor are tilted relative to one another in a constant-displacement machine. The rotor and the piston disk are furthermore coupled to one another for conjoint rotation by means of a driving device. This coupling can also be implemented indirectly by means of a drive shaft of the machine. According to the disclosure, a sliding joint axial with respect to a drive shaft is arranged between the rotor and the piston disk. This ensures decoupling and axial mobility of the piston disk relative to the rotor.

The axial sliding joint can have a key and a groove or toothing, for example.

The driving device can be arranged inside or outside a pitch circle of the sections and pistons. At the outer circumference of the pitch circle, the circumferential forces to be transmitted are lower, and therefore the driving device can have comparatively small individual elements (e.g. journals). In this case, the drive shaft can be continuous.

To support an axial preloading force, which is required between the piston disk and the rotor, a pressure sleeve can be arranged on (e.g. pushed onto) the outer circumference of the drive shaft, said sleeve having on its outer circumference a spherical shape against which the piston disk or the rotor rests.

In a preferred principle of the axial piston machine according to the disclosure, the rotor is arranged perpendicularly to the drive shaft and is connected to the latter for conjoint rotation or is formed integrally therewith, while the piston disk can be tilted or is tilted relative to the drive shaft.

The piston disk can be provided with a bushing-type extension, which is part of the driving device or which is used to articulate the driving device thereon.

In an illustrative embodiment which is simple in terms of device design, the driving device has a joint having just one transverse axis. According to a first variant, two journals are arranged along the transverse axis, said journals being inserted into two mutually opposite axial slotted holes or grooves in such a way as to be pivotable and slidable. According to a second variant, a continuous pin is arranged along the transverse axis, said pin being inserted into two mutually opposite axial slotted holes or grooves in such a way as to be pivotable and slidable.

In a Cardan-like illustrative embodiment, the driving device has two joints having respective transverse axes, wherein the two transverse axes are set at 90 degrees to one another. According to a first variant, two journals are in this case arranged along each transverse axis, said journals being inserted into two mutually opposite axial slotted holes or grooves in such a way as to be pivotable and slidable. In this case, the two transverse axes can intersect, i.e. form a cross. According to a second variant, a continuous pin is arranged along each transverse axis, said pin being inserted into two mutually opposite axial slotted holes or grooves.

To reduce frictional losses, laterally flattened sliding blocks or sliding bushings can be placed on end sections of the two or four journals or on the pin or pins, said sliding blocks being pivotable or rotatable relative to the journal or to the pin or pins about the transverse axis and being inserted in a sliding manner into the slotted holes or grooves.

In another illustrative embodiment, the driving device has at least one Cardan joint known per se from the prior art, the central part of which has two transverse axes, which intersect and are perpendicular to one another and along each of which two journals inserted pivotably into holes extend.

In a development of the Cardan joint, the central part thereof can be an intermediate sleeve which is annular, for example, which is arranged between an outer circumference of the drive shaft of or the rotor and an inner circumference of the piston disk or the bushing-type extension thereof. In this case, the intermediate sleeve can be connected in an articulated manner to the rotor by means of two mutually opposite inner journals and can be connected in an articulated manner to the piston disk by means of two mutually opposite outer journals, for example.

Particularly in the case of relatively large tilting angles of the piston disk, it is preferred if the driving device has a central bushing, which, on the one hand, is articulated on the drive shaft or on the rotor and, on the other hand, is articulated on the piston disk or the bushing-type extension thereof. This enables the central bushing to adopt a tilt relative to the drive shaft corresponding to half the tilt of the piston disk.

In this arrangement, the two articulations can be embodied by respective Cardan joints with intermediate sleeves as described above, for example.

The central bushing can also be articulated on the drive shaft or on the rotor by means of two rotary-sliding connectors and can be articulated on the piston disk or the extension thereof by means of two rotary-sliding connectors offset by 90 degrees relative to said rotary-sliding connectors. The rotary-sliding connectors each have a sliding block which is guided in an axial slotted hole or an axial groove, and they each have a journal which is inserted pivotably into a hole.

In another preferred illustrative embodiment, the driving device is formed by a plurality of radially inward-directed projections, e.g. webs, which are each arranged on a cylinder sleeve and which remain engaged in axial grooves of the piston disk or of the extension thereof during revolution or can be engaged therein during revolution in order in this way to transmit the torque. In this illustrative embodiment, no additional components are required for the driving device.

In another preferred illustrative embodiment, the driving device has a constant velocity joint or homokinetic joint, which has a plurality of balls, wherein each ball is guided in a first and a second groove.

In this case, the balls can be guided in a cage, thereby making possible pairs of grooves which are not capable alone of determining the position of the common ball thereof.

In another preferred illustrative embodiment, the driving device has at least two balls or spherical segments distributed over the circumference, which are each guided along a first straight track set obliquely to the drive shaft (or to the rotor) and along a second straight track set obliquely to a longitudinal axis of the piston disk. In an embodiment as a bipot joint, two mutually opposite balls or spherical segments are provided.

In this case, a pin can be provided, which extends along the first track. According to a first variant, the ball or spherical segment is secured on the pin, and the pin can be moved along the first track. According to a second variant, the pin is secured on the drive shaft or on the rotor, while the ball or spherical segment can be moved along the pin and hence along the first track.

As an alternative, it is also possible for each ball to be guided along the first track and along the second track by two grooves in each case.

The driving device can be a tripot joint having three spherical segments, which are each guided so as to be movable on one of three radial journals of the drive shaft or of the rotor, said radial journals being distributed uniformly over the circumference, and which are each guided so as to be movable in two mutually opposite axial grooves of the piston disk.

It is also possible to provide two tripot joints of this kind, of which a first tripot joint connects the drive shaft or the rotor in an articulated manner to the central bushing, and wherein the second tripot joint connects the central bushing in an articulated manner to the piston disk.

In another preferred illustrative embodiment which is simple in terms of device design, the driving device is formed by the spherical or ball-shaped sections inserted in the cylinder sleeves and by the cylinder sleeves and by necks of the pistons. The necks are preferably of tapered shape for this purpose.

In another illustrative embodiment, the driving device has a plurality of recesses, which are distributed over the circumference of the rotor, for example, and into which corresponding pins, which are secured on the piston disk, for example, engage during revolution.

In another illustrative embodiment, the driving device has a curved toothing, which is formed on the drive shaft or on the rotor, on the one hand, and on the piston disk, on the other hand. In the case of a constant-displacement machine, the toothing can be of tapered configuration.

The driving device can also have a flexible element or an element which can be bent according to the tilt of the drum disk. This element can be a bellows, for example.

BRIEF DESCRIPTION OF THE DRAWINGS

Various illustrative embodiments of a hydrostatic axial piston machine according to the disclosure are described in detail below with reference to the figures.

In the drawings:

FIG. 1 shows essential parts of a first illustrative embodiment in a schematic longitudinal section,

FIG. 2 shows a detail of a second illustrative embodiment in a transparent perspective view,

FIG. 3 shows a detail of a third illustrative embodiment in a longitudinal section,

FIG. 4 shows a detail of a fourth illustrative embodiment in a longitudinal section,

FIG. 5 shows a detail of a fifth illustrative embodiment in a longitudinal section,

FIG. 6 shows a detail of a sixth illustrative embodiment in a longitudinal section,

FIG. 7 shows a detail of a seventh illustrative embodiment in a transparent perspective view,

FIG. 8 shows a detail of an eighth illustrative embodiment in a perspective view,

FIG. 9 shows a detail of a ninth illustrative embodiment in a longitudinal section,

FIG. 10 shows essential parts of a tenth illustrative embodiment in a longitudinal section,

FIG. 11 shows a detail of an eleventh illustrative embodiment in a transparent perspective view,

FIG. 12 shows a detail of a twelfth illustrative embodiment in a transparent perspective view,

FIG. 13 shows a detail of a thirteenth illustrative embodiment in a transparent perspective view, and

FIG. 14 shows a detail of a fourteenth illustrative embodiment in a perspective view.

DETAILED DESCRIPTION

FIG. 1 shows the essential parts of a first illustrative embodiment of a hydrostatic axial piston machine according to the disclosure. It has a drive shaft 1, to which a disk-shaped rotor 2 is coupled for conjoint rotation. Uniformly distributed spherical segments 4 are secured on the circumference thereof, onto each of which segments a cylinder sleeve 6 is pushed in such a way that they jointly form a ball joint. A spherical piston 8 is furthermore inserted into each cylinder sleeve 6, with the result that the spherical segment 4 delimits a displacer chamber 10 together with the piston 8. Each piston 8 is secured by means of a neck 12 on a piston disk 14, which is set at an angle to the rotor 2 and hence to the drive shaft 1.

During revolution of the drive shaft 1 with the rotor 2, the piston disk 14 and with the cylinder sleeves 6, the pistons 8 perform a stroke motion relative to the respective cylinder sleeve 6. In this case, the spherical pistons 8 are inserted pivotably in the respective cylinder sleeves 6. The piston disk 14 is pushed in the direction of the rotor 2 (to the left in FIG. 1) against an annular pressure sleeve 15, which is mounted on the drive shaft 1 and is supported there on a radial shoulder (not shown).

By means of an axial sliding joint according to the disclosure, which is designed as a groove-key arrangement 16 between the rotor 2 and the drive shaft 1 in the first illustrative embodiment according to FIG. 1, the axial decoupling of the rotor 2 from the piston disk 14 is achieved.

Driving is accomplished by means of the displacer unit having the three contact partners: spherical segment 4, cylinder sleeve 6 and neck 12. In this case, the necks 12 are configured in such a way that, at one of the pistons 8, there is always surface contact between the neck 12 thereof and the associated cylinder sleeve 6, via which the torque is transmitted. The driving piston 8 changes during one revolution of the illustrative embodiment shown in FIG. 1.

FIG. 2 shows a detail of a second illustrative embodiment of the axial piston machine according to the disclosure in a transparent perspective view. The rotor (not shown in FIG. 2) is supported on the drive shaft 1 by means of toothing 116. The piston disk 114 is developed to give a piston drum, which has a bushing-type extension 120. Two mutually opposite slotted holes 122 are introduced into said extension. A pin 124 is inserted transversely into the drive shaft 1, respective sliding blocks 126 being secured rotatably on each of the end sections of said pin which project from the drive shaft 1. The sliding blocks 126 are secured on the pin 124 by means of wire rings 128.

The piston disk 114 is driven by means of flattened outer regions of the sliding blocks 126, which are in contact with one of two contact surfaces of the slotted holes 122. As an alternative, the pin can also be secured in the rotor instead of in the drive shaft. Moreover, the pin can be introduced into the piston disk or into the extension and the contact surfaces can be introduced into the rotor. As a supplement to the second illustrative embodiment according to FIG. 2, it is also possible for two pins 124 with a total of four sliding blocks 126 to be provided, wherein the two pins 124 are arranged crosswise relative to one another. To transmit the axial preloading force, there is furthermore a need for a spherical cap, which is positioned between the pressure sleeve 15 and the piston disk 114, for example.

FIG. 3 shows a third illustrative embodiment according to the principle of a Cardan joint, wherein only a short section of the drive shaft 1 and only an end section of the extension 120 of the piston disk 114 are shown. A sleeve-shaped section of the rotor 102 is shown on the drive shaft 1. An annular intermediate sleeve 130 is provided between said section and the extension 120. With the rotor 102, this forms a first axis of rotation (situated in the plane of the drawing) and, with the extension 120, it forms a second axis of rotation perpendicular thereto (arranged perpendicularly to the plane of the drawing). For this purpose, four pins (not shown in FIG. 3) are provided, being inserted into corresponding holes.

FIG. 4 shows a fourth illustrative embodiment, in which two Cardan joints based on the principle of the illustrative embodiment shown in FIG. 3 and also a central bushing 132 associated therewith are provided. The two intermediate sleeves 130 are pinned to the central bushing 132 perpendicularly to the plane of the drawing, thus allowing rotation about the pin axis. A similar rotary connection, which is perpendicular thereto in each case, is established between the rotor 102 and one intermediate sleeve 130 and between the piston disk 114 and the other intermediate sleeve 130.

In the third illustrative embodiment and in the fourth illustrative embodiment, axial decoupling is ensured by introducing a groove-key arrangement 16 according to FIG. 1.

FIG. 5 shows a fifth illustrative embodiment, in which the driving device is formed by a ball-type constant velocity joint. This has a plurality of balls 234, which are guided in straight axial ball races. To be more precise, each ball 234 has a first groove 236 formed in the rotor 202 and a second groove 237 formed in the extension 220 of the piston disk. All the grooves 236, 237 extend axially with respect to the respective component 202, 220, in which they are arranged. As an alternative to the grooves 236, 237 shown in FIG. 5, said grooves can also be curved.

Since the shape of the grooves 236, 237 does not unambiguously determine the position of the associated balls 234 in the fifth illustrative embodiment according to FIG. 5, a cage 238 is used for definite guidance of the balls 234. The cage 238 is configured in such a way that the rotation of the rotor 202 and of the piston disk take place synchronously. The pressure sleeve 15 is provided for transmission of the axial force, being clamped between the rotor 202 and the cage 238.

According to another basic variant, the driving device is formed by a plurality of pots, the balls 244 of which each run on two obliquely set straight tracks.

FIG. 6 shows an illustrative embodiment in which a plurality of spherical segments 240 are guided in such a way as to be movable along a respective pin 241 secured on the rotor 202 and set obliquely to the latter. Each spherical segment 240 is furthermore guided along a track 242 set obliquely to a longitudinal axis of the piston disk 214. As an alternative, the spherical segment can be secured on the pin, which is then supported in an axially movable manner in the rotor. The rotor and the piston disk can furthermore be exchanged.

FIG. 7 shows a seventh illustrative embodiment, in which a ball 244 is, on the one hand, guided along a track set obliquely to the longitudinal axis of the rotor 202 by means of two mutually opposite grooves 245. On the other hand, the ball 244 is guided along the track set obliquely to the longitudinal axis of the piston disk 214, likewise by means of two mutually opposite grooves 246. The pairs of grooves 245, 246 are formed in respective pairs of guide rails, which are inserted into the rotor 202 and into the piston disk 214. A pressure sleeve 15 (not shown in FIG. 7) is used to transmit the axial force. The axial sliding joint is formed by the toothing 116.

FIG. 8 shows an eighth illustrative embodiment, in which the driving device is designed as a tripot joint. In this case, three radial journals 248 uniformly distributed over the circumference are secured on the rotor 202, on each of which a spherical segment 240, e.g. an annular spherical segment, is rotatably supported. The extension 220 of the piston disk 214 has three axial slotted holes, in which pairs of mutually facing grooves 245, 246, 247 are arranged. These pairs of grooves 245, 246, 247 each guide one spherical segment 240. A pressure sleeve 15 (not shown in FIG. 8) is used to transmit the axial force. It is also possible to provide a double tripot joint between the drive shaft 1 and the piston disk 214 or the extension 220 thereof, said joint consisting of two tripot joints according to FIG. 8.

FIG. 9 shows a detail of a ninth example, in which the driving device between the rotor 202 and the extension 220 of the piston disk has two or more pins 250, which extended radially inward from the inner circumference of the extension 220. The pins 250 project into corresponding recesses 252 in the rotor 202. Driving is in each case accomplished by means of those pins 250 which are in contact with the rotor 202. As an alternative, it is also possible for the pins to be provided in the rotor and for the recesses to be provided in the piston drum or in the extension thereof. The axial forces are transmitted by a separate component similar to the pressure sleeve 15 from FIG. 2.

FIG. 10 shows a tenth illustrative embodiment of the axial piston machine according to the disclosure. The rotor 302 thereof is connected for conjoint rotation to the drive shaft 1 by means of the toothing 116. Circular-cylindrical necks 312, on which the pistons 8 are formed, are inserted into the piston disk 314, which is tilted relative to said shaft. Between the rotor 302 and the piston disk 314 there are two individual Cardan joints. The intermediate sleeves 330 thereof are both pinned to a central bushing 332, allowing rotation about the pin axis. A similar rotary connection is established between the rotor 302 and the associated intermediate sleeve 330 and between the piston disk 314 and the associated intermediate sleeve 330. The axial preloading force can be transmitted by means of a spring (not shown) between an axially movable component 354 and the piston disk 314, for example.

FIG. 11 shows a detail of an eleventh illustrative embodiment having a driving device, in which a sleeve-type extension of the rotor 302 engages around an extension 220 of the piston disk. An individual Cardan joint having two joint connections is situated between them. On the one hand, there is a rotary-sliding connection with two partners and a rotary-sliding connection offset by 90° thereto in the direction of rotation, likewise with two partners. FIG. 11 shows a solution by means of four flattened pins 356, wherein a main section of a journal 356 and a foot section of another journal 356 are shown in FIG. 11. Each journal 356 is guided on one side in a bore and on the other side in a slotted hole 122. To transmit the axial preloading force, there is furthermore a need for a spherical cap, which is positioned between the drive shaft and the piston drum, for example.

In the illustrative embodiment according to FIG. 12, two individual Cardan joints according to FIG. 11 and a central bushing 432 are provided as a driving device. The uniform torque transmission of the rotor 402 to the piston drum, of which only the extension 220 is shown in FIG. 12, is ensured by the fact that a central axis of the central bushing 432 assumes the same angle in each case to the axis of the rotor 402, on the one hand, and to the axis of the extension 220 and hence of the piston disk, on the other hand.

FIG. 13 shows a thirteenth illustrative embodiment, in which the driving device is formed by a double Cardan of compact construction. Between the rotor 402 and the extension 220 of the piston disk there is a central bushing 532, which is connected to the rotor 402 by means of two rotary-sliding connectors 558, on the one hand, and to the extension 220 by means of rotary-sliding connectors 558 arranged offset by 90° thereto, on the other hand. Each rotary-sliding connector 558 has a journal, by means of which it is inserted into a corresponding hole, and a sliding block, which is inserted into a corresponding slotted hole 122. This arrangement makes it possible to introduce the slotted holes 122 in the central bushing 532 offset by 90° relative to the holes, enabling the central bushing 532 to be of compact configuration without sacrificing rigidity. The angular position of the central bushing 532 and hence the uniform torque transmission and the transmission of the axial preloading force are ensured as in the twelfth illustrative embodiment according to FIG. 12.

FIG. 14 shows a fourteenth illustrative embodiment of the axial piston machine according to the disclosure, wherein only one cylinder sleeve 606 is shown between the piston disk 314 and the rotor 402 for the sake of clarity. On its side facing the extension 620 of the piston disk 314, each cylinder sleeve 606 has a radially inward-directed projection 660, which extends approximately along the cylinder sleeve 606. Corresponding axial grooves 662 are introduced on the outer circumference of the extension 620, wherein the projection 660 of the associated cylinder sleeve 606 engages in the groove 662, depending on its rotational position. In this case, the driving device is formed by the projections 660 and the grooves 662 without the need to provide special components for driving.

A disclosure is made of a hydrostatic axial piston machine having a drive shaft and having a plurality of cylinder sleeves, in which a spherical or ball-shaped section, on the one hand, and a spherical or ball-shaped piston, on the other hand, are inserted in order to delimit a respective displacer chamber. The sections are secured on a rotor, while the pistons are secured on a piston disk or piston drum. Depending on the embodiment, the piston disk can be tilted at different pivoting angles relative to the rotor in a variable-displacement machine, or the piston disk is tilted continuously relative to the rotor in a constant-displacement machine. The rotor and the piston disk are coupled to one another for conjoint rotation by means of a driving device. This coupling can also be implemented indirectly by means of a drive shaft of the machine. A sliding joint axial with respect to a drive shaft is arranged between the rotor and the piston disk.

LIST OF REFERENCE SIGNS

• 1 drive shaft
• 2; 102; 202; 302; 402 rotor
• 4 spherical segment
• 6; 606 cylinder sleeve
• 8 spherical piston
• 10 displacer chamber
• 12; 312 neck
• 14; 114; 214; 314 piston disk
• 15 pressure sleeve
• 16 groove-key arrangement
• 116 toothing
• 120; 220; 620 extension
• 122 slotted hole
• 124 pin
• 126 sliding block
• 128 wire ring
• 130; 330 intermediate sleeve
• 132; 332; 432; 532 central bushing
• 234 ball
• 236 first groove
• 237 second groove
• 238 cage
• 240 spherical segment
• 241 pin
• 242 track
• 244 ball
• 245, 246, 247 groove
• 248 radial journal
• 250 pin
• 252 recess
• 354 axially movable component
• 356 journal
• 558 rotary-sliding connector
• 660 projection
• 662 groove

Claims

1. A hydrostatic axial piston machine, comprising:

a drive shaft;

a rotor having a plurality of spherical or ball-shaped sections arranged thereon;

a piston disk having a plurality of pistons arranged thereon, the piston disk being configured to be tilted relative to the rotor or the rotor being configured to be tilted relative to the piston disk;

a plurality of cylinder sleeves with each cylinder sleeve having a respective section of the rotor and a respective piston of the piston disk inserted therein to define a respective displacer chamber; and

a driving device configured to couple the piston disk and the rotor for conjoint rotation,

wherein an axial sliding joint is arranged between the rotor and the piston disk.

2. The hydrostatic axial piston machine according to claim 1, wherein the rotor is arranged perpendicularly to the drive shaft and is one of connected to the drive shaft for conjoint rotation or formed integrally therewith, and wherein the piston disk is configured to be tilted relative to the drive shaft.

3. The hydrostatic axial piston machine according to claim 1, wherein the driving device has a joint having a transverse axis, wherein two journals are arranged along the transverse axis, the journals being inserted into two mutually opposite axial slotted holes or grooves, or wherein a pin is arranged along the transverse axis, the pin being inserted into two mutually opposite axial slotted holes or grooves.

4. The hydrostatic axial piston machine according to claim 1, wherein the driving device has two joints having respective transverse axes, and wherein the two transverse axes are set at 90 degrees to one another, and wherein two journals are arranged along each transverse axis, the journals being inserted into two mutually opposite axial slotted holes or grooves, or wherein a continuous pin is arranged along each transverse axis, the pin being inserted into two mutually opposite axial slotted holes or grooves.

5. The hydrostatic axial piston machine according to claim 3, wherein laterally flattened sliding blocks are placed on end sections of the journals or on the pin or pins, the sliding blocks being pivotable about the transverse axis and being inserted into the slotted holes or grooves in a sliding manner.

6. The hydrostatic axial piston machine according to claim 1, wherein the driving device has at least one Cardan joint, the Cardan joint having a central part with two transverse axes, along each of which two journals inserted into holes extend.

7. The hydrostatic axial piston machine according to claim 6, wherein the central part is an intermediate sleeve arranged between an outer circumference of the drive shaft or the rotor and an inner circumference of the piston disk or an extension thereof.

8. The hydrostatic axial piston machine according to claim 1, wherein the driving device has a central bushing that is articulated on the drive shaft or on the rotor and that is articulated on the piston disk or an extension thereof.

9. The hydrostatic axial piston machine according to claim 8, wherein the central bushing is articulated on the drive shaft or on the rotor by two rotary-sliding connectors and is articulated on the piston disk or an extension thereof by two rotary-sliding connectors offset by 90 degrees relative to the rotary-sliding connectors, wherein the rotary-sliding connectors each have a sliding block that is guided in an axial slotted hole or an axial groove, and wherein the rotary-sliding connectors each have a journal that is inserted into a hole.

10. The hydrostatic axial piston machine according to claim 1, wherein the driving device is formed by a plurality of radially inward-directed projections, the radially inward-directed projections each being arranged on a cylinder sleeve and being configured to be engaged in axial grooves of the piston disk or of an extension thereof.

11. The hydrostatic axial piston machine according to claim 1, wherein the driving device is a constant velocity joint having a plurality of balls, and wherein each ball is guided in a first groove and a second groove.

12. The hydrostatic axial piston machine according to claim 1, wherein the driving device has at least two balls or spherical segments that are each guided along a first track set obliquely to the drive shaft and along a second track set obliquely to a longitudinal axis of the piston disk.

13. The hydrostatic axial piston machine according to claim 12, further comprising a pin extending along the first track.

14. The hydrostatic axial piston machine according to claim 12, wherein each ball is guided along the first track and along the second track by two grooves, respectively.

15. The hydrostatic axial piston machine according to claim 1, wherein the driving device is a tripot joint having three spherical segments, which are each guided so as to be movable on one of three radial journals of the drive shaft or of the rotor, the radial journals being distributed uniformly over the circumference, and which are each guided so as to be movable in two axial grooves of the piston disk.

16. The hydrostatic axial piston machine according to claim 1, wherein the driving device is formed by the spherical or ball-shaped sections and by the cylinder sleeves and by necks of the pistons.

17. The hydrostatic axial piston machine according to claim 1, wherein the driving device has a plurality of recesses into which corresponding pins are configured to be engaged.

18. The hydrostatic axial piston machine according to claim 1, wherein the driving device has a curved toothing on the drive shaft or on the rotor and on the piston disk.

19. The hydrostatic axial piston machine according to claim 1, wherein the driving device has a flexible element.