EP2937567A2 - Hydrostatic axial piston engine with inclined axes, with a slave joint for driving the cylinder barrels - Google Patents

Abstract

The invention relates to a hydrostatic axial piston machine (1) in bent-axis design with a about a rotational axis (R t) rotatably within a housing (2) arranged drive shaft (4) which is provided with a drive flange (3), and one about an axis of rotation (R z) rotatably within the housing (2) of the axial piston machine (1) arranged cylinder drum (7), wherein the cylinder drum (7) is provided with a plurality Kolbenausnehmungen (8), in each of which a piston (10) is longitudinally displaceable, wherein the piston (10) are hinged to the drive flange (3), and wherein between the drive shaft (4) and the cylinder drum (7) a driving joint (30) for driving the cylinder drum (7) is arranged, wherein the driving joint (30) at least one has a driving body (M1, M2, M3, M4), which is supported in the drive shaft (4) and the cylinder drum (7). According to the invention, a lubrication device (80) for the driving joint (30) is provided by means of which the driving body (M1; M2; M3; M4) has lubricant for cooling and lubricating the driving body (M1; M2; M3; M4) from a housing (2) ) of the axial piston machine (1) arranged lubricant connection (81) can be fed.

Description

The invention relates to a hydrostatic axial piston machine in oblique-axis construction with a about a rotation axis rotatably disposed within a housing drive shaft, which is provided with a drive flange, and about a rotation axis rotatably disposed within the housing of the axial piston cylinder cylinder, wherein the cylinder drum is provided with a plurality Kolbenausnehmungen in each of which a piston is arranged to be longitudinally displaceable, wherein the pistons are articulatedly secured to the drive flange, and wherein between the drive shaft and the cylinder drum, a follower joint for entrainment of the cylinder drum is arranged, wherein the follower joint has at least one designed as sliding body or as a rolling body entrainment body, which is supported in the drive shaft and the cylinder drum.

In hydrostatic axial piston machines in bent-axis design, the piston arranged longitudinally displaceably in the cylinder drum are usually fastened by means of a ball joint to the drive flange of a drive shaft. The piston forces are based here on the piston on the drive shaft located on the drive flange and generate a torque. In axial piston machines in Schrägachsenbauweise principle takes place in a rotation no entrainment of the cylinder drum with the piston arranged therein. For the entrainment of the cylinder drum a follower joint is required, which is arranged between the drive shaft and the cylinder drum. It is already known to use a follower joint according to the Rzeppa principle or the tripod principle, in which the entrainment of the cylinder drum by means of at least designed as a rolling element or sliding body driving body, which transmits a torque between the drive shaft and cylinder drum for driving the cylinder drum ,

Generic axial piston machines in bent-axis design have compared to axial piston machines in swash plate design significantly higher maximum allowable Speeds up, so that axial piston machines in Schrägachsenbauweise for use as a hydraulic motor advantages.

In hydrostatic axial piston machines, the housing, within which the rotating drive shaft and the rotating cylinder drum are arranged, is generally filled with pressure medium, for example hydraulic oil, in order to ensure cooling and lubrication of the components. During operation of the axial piston machine with rotating drive shaft and rotating cylinder drum, this causes churning losses, which increase disproportionately with increasing speed. These churning losses represent an additional energy consumption, which must be provided by the drive as unwanted power loss in an axial piston machine designed as a pump or is not available as output power in an axial piston machine designed as a motor. In particular, at high rotational speeds of the rotating components, this power loss can take on a considerable size, which in Axialkolbenmaschinen the performance and operational capability are limited to high speeds out and limited.

To avoid these disadvantages, it is already known to drain the housing of a hydrostatic axial piston machine of pressure medium in order to reduce the losses caused by the splashing of the rotating components and to increase the efficiency of the axial piston machine at higher speeds.

In a hydrostatic axial piston machine in axial piston machine with a pressure-fluid-empty housing, however, a sufficient cooling and lubrication of the driving body of the driving joint is no longer given.

The present invention has for its object to provide a generic axial piston machine is available, which is operable with a pressure-fluid-depleted housing and at the same time has sufficient lubrication and cooling of the driving body of the follower joint.

This object is achieved in that a lubricating device is provided for the driving pin, by means of the driving body lubricant for cooling and lubrication of the driving body of a arranged on the housing of the axial piston lubricant supply can be supplied is. With such a lubricating device of the follower joint, the driving body of the driving joint can be supplied with lubricant, for example hydraulic oil, which is supplied via a lubricant connection to the housing of the axial piston machine in a simple manner and with low construction costs, so that during operation of the axial piston machine with a pressure-fluid-exhausted housing for the operation of the machine, in particular at high speeds, sufficient cooling and lubrication of the driving body of the driving joint is made possible by the lubricant supplied via the lubricating device.

A supply of the driving body of the driving joint with lubricant, which is supplied via the lubricant connection to the housing, can be ensured with low construction costs, if according to an advantageous embodiment of the invention, the lubricating device is arranged in the drive shaft and has a arranged in the drive shaft lubricant channel. During operation of the axial piston machine with a pressure-medium-exhausted housing, lubricant can be guided from the lubricant connection on the housing to the driving bodies of the driving joint in a simple manner via a lubricant channel arranged in the drive shaft.

According to an advantageous embodiment of the invention, the lubricant passage has a lubricant supply hole arranged in the drive shaft, which is connected to the lubricant port, and at least one arranged in the drive shaft lubrication hole which is connected to the Schiermittelversorgungsbohrung and which extends to the peripheral surface of the drive shaft and in the Peripheral surface is provided with an opening, wherein the opening of the lubrication hole in the peripheral surface is arranged such that upon rotation of the drive shaft via the lubricant supply bore and the lubrication hole supplied lubricant flows through the centrifugal force occurring on the driving body. To supply the driving body of the driving joint with lubricant thus a lubricant supply hole is introduced in the drive shaft of the axial piston machine. At this lubricant supply bore a transverse bore is connected as a lubricating hole for each driving body, which is arranged in the drive shaft and which is provided on the outer circumference of the drive shaft with an opening through which the lubricant supplied via the lubricant supply bore lubricant and directly to the associated driving body of the driving joint can flow. A lubricant supply bore and corresponding lubrication holes designed as transverse bores can be produced in the drive shaft of the axial piston machine with low construction costs. In a rotation of the drive shaft is thus achieved that lubricant flows through the centrifugal force on the driving body, so that the driving body can be lubricated and cooled in a simple manner with rotating drive shaft of the supplied via the lubricant supply hole and the lubrication hole and the driving body onströmendem lubricant.

According to one embodiment of the invention, the driving body is received in a bed of the drive shaft and in a bedding of the cylinder drum. With the lubricating device according to the invention in this case a targeted supply of the lubricant to the driving body in the region of the two bedding is possible.

With particular advantage, the lubrication hole is directed to the driving body. As a result, it is achieved in a simple manner that the lubricant supplied via the lubricant supply bore and the lubrication bore flows directly onto the driver bodies through the centrifugal force, so that the driver bodies are targeted by lubricant and can be specifically cooled and lubricated with a small amount of lubricant.

According to the driving torque to be transmitted between the drive shaft and the cylinder drum for driving the cylinder drum, it may be sufficient for small driving torques to be transmitted to provide a single driving body. For higher to be transmitted driving torques between the drive shaft and the cylinder drum, the number of driving bodies can be increased. If a plurality of distributed over the circumference arranged driving body is provided over the circumference, a lubricating hole is advantageously provided for each driving body. As a result, it is achieved in a simple manner that lubricant can flow to each driving body via the associated lubrication hole for cooling and lubrication, so that the several driving bodies of the driving joint can be reliably cooled and lubricated with a small amount of lubricant.

According to an advantageous embodiment of the invention, the lubricant supply bore is formed as a coaxial with the axis of rotation of the drive shaft arranged longitudinal bore in the drive shaft. A coaxial and thus formed as a central bore in the drive shaft longitudinal bore can be made with low construction costs.

According to an advantageous development of the invention, the lubricant supply bore extends to a bearing device, by means of which the drive shaft is rotatably mounted in the housing. As a result, a connection of the lubricant supply bore with the lubricant connection arranged on the housing can be produced in a simple manner.

With particular advantage, according to one embodiment of the invention, the drive shaft is mounted in the housing on both sides of the cylinder drum, the bearing of the drive shaft in the housing comprises a drive flange side bearing device and a cylinder drum side bearing means, wherein the lubricant supply bore extends to the cylinder drum side bearing means. In a Schrägachsen axial piston machine is usually the drive or output torque of the axial piston on the drive flange side of the drive shaft, which is mounted on the triebflanschseitige bearing device in the housing, supplied or removed, so that the cylindrical drum-side portion of the drive shaft, via the Cylinder drum side bearing device is mounted in the housing, is less loaded. The arrangement of the lubricant channel in the cylinder drum-side region of the drive shaft thus results in advantages, since the drive shaft is not weakened by the lubricant supply bore and the lubrication holes with respect to the transmission of the drive or output torque and must be increased in diameter.

According to a preferred embodiment of the invention, the lubricant supply bore is provided in the region of the bearing device with a feed opening, which is connected to the lubricant connection arranged on the housing of the axial piston machine. With such a supply opening can easily with the lubricant supply hole connected to the housing of the axial piston engine arranged lubricant port to supply the lubricating device with lubricant.

With regard to a low construction cost, there are advantages if the feed opening is formed on an axial end face of the drive shaft.

According to an advantageous embodiment of the invention, a lubricant space is formed between the bearing device, the end face of the drive shaft and the housing, which is in communication with the lubricant connection. This makes it possible in a simple manner, which is supplied via the lubricant connection to the housing lubricant supplied both for lubrication and cooling of the driving body of the follower joint as well as for lubrication and cooling of the bearing device of the drive shaft. During operation of the axial piston machine with a pressure-medium-exhausted housing, cooling and lubrication of the cylinder-drum-side bearing device of the drive shaft and the driving body of the driving joint can thus be achieved with little construction effort.

According to a preferred embodiment of the invention, each driving body is designed as a driving body pair with two half-bodies, which are arranged alternately in the drive shaft and the cylinder drum and abut each other by means of contact surfaces. The driving body pair in this case has in each case one belonging to the cylinder drum cylindrical side half body and belonging to the drive shaft drive shaft side half body, wherein the cylinder drum side half body of Mitnahmekörperpaars is taken in a bedding of the cylinder drum and the drive shaft side half body of Mitnahmekörperpaars in a ballast of the drive shaft.

With the lubricating device according to an advantageous embodiment of the invention, the half-bodies in the area of the contact surfaces and / or in the area of the bedding lubricant can be supplied. The half-bodies of the driving body pair can thus be cooled and lubricated with the lubrication device according to the invention in a simple manner on the contact surfaces as well as on the surfaces with which the half-bodies are arranged in the beddings.

According to a preferred embodiment of the invention, the driving pin is formed as a rotationally synchronous driving joint for rotationally synchronous rotation of the cylinder drum and the drive shaft. With a rotationally synchronous entrainment of the cylinder drum, a uniform drive or output torque is achieved on the drive shaft and it can be the component loads of the axial piston machine can be reduced. In addition, the noises of the axial piston machine and of a drive train coupled to the axial piston machine are reduced with a rotationally synchronous driving joint.

According to an advantageous embodiment of the invention, the follower joint is designed as a cone beam half-roll joint, which has at least one pair of rollers as Mitnahmekörperpaar with two semi-cylindrical half-rollers as a half body, wherein the semi-cylindrical half-rollers are flattened to a rotational axis and the half-rollers on the flattened sides planar sliding surfaces as Berührflächen form, at which the half rollers of the roller pair abut to form a surface contact. With a trained as a cone beam half-roll joint driving joint driving the cylinder drum can be achieved in an axial piston oblique-axis design with low construction costs for the driving joint. Such a cone-beam half-roll joint between the drive shaft and the cylinder drum can be performed in a simple manner by appropriate geometric design as homokinetic constant velocity joint, in which an exact and uniform and thus rotationally synchronous entrainment of the cylinder drum. In addition, in a arranged between the drive shaft and the cylinder drum cone beam half-roll joint as entrainment joint for the entrainment of the cylinder drum in a simple way, the drive shaft through the cylinder drum or the axial piston machine are passed in the axial direction to store the drive shaft on both sides of the cylinder drum can. In a cone-beam half-roll joint, the half rolls of each pair of rolls are arranged in pairs. The half-rollers of a pair of rollers of the conical-beam half-roller joint are essentially formed up to the axis of rotation and thus flattened to the longitudinal axis of the cylindrical bodies. By flattening arise on the flattened sides of the half-rollers flat sliding surfaces as contact surfaces against which the two half-rollers of a pair of rollers abut each other and where the force is transmitted over a surface contact between the flat surfaces. With such pairs of rollers, each of consist of two semi-cylindrical half rollers whose half rollers are flattened to a rotational axis and thus the longitudinal axis of the half rollers and which lie against each other on the flattened sides to form a surface contact and flat sliding surfaces, the forces and thus the torque to take the cylinder drum with low construction costs be transferred, since the half rollers are simple and inexpensive to produce. The fact that the contact surfaces between the two half rollers of a pair of rollers are formed as flat sliding surfaces and a surface contact between the two half rollers of a pair of rollers for power transmission occurs, even at high forces to be transferred when taking the cylinder drum low Hertzian pressure. The cone beam half-roll joint formed by corresponding pairs of rolls is therefore still robust against overload, which can arise, for example, by a high rotational acceleration. In the embodiment of the axial piston machine according to the invention as a hydraulic motor, the axial piston machine according to the invention can thus also be used in applications with high rotational accelerations. With the lubrication device according to the invention in this case the lubricant for cooling and lubrication can be supplied to the two half-rollers in the area of the contact surfaces formed as a flat sliding surfaces during operation of the axial piston machine with a pressure-medium-empty housing.

Particular advantages arise when according to an embodiment of the invention, the driving body, in particular the half rollers, is arranged in the radial direction within the piston and spaced from the axes of rotation of the drive shaft and the cylinder drum. The preferred trained as a cone beam half-roll joint follower joint is thus disposed within the ring and the pitch circle of the pistons, whereby a space-saving design of the axial piston is achievable and targeted lubricant lubricant can be supplied to the driving bodies by the centrifugal force effect for cooling and lubrication on the formed in the drive shaft lubricant channel , In addition, the driving body, for example, half rolls of the pairs of rollers, perpendicular to the axis of rotation of the drive shaft and the axis of rotation of the cylinder drum, so that at the contact surfaces formed by the flat sliding surfaces and thus the contact surfaces, the torque can be transmitted to take the cylinder drum. This arrangement of the driving body of the Mitnahmegelenks, in particular the half-rollers of the cone beam half-roll joint, also makes it possible in a simple manner to provide the follower joint with a concentric with the axis of rotation of the cylinder drum longitudinal recess to pass the drive shaft through the cylinder drum for two-sided storage and arranged the driving body by means of a drive shaft Lubricant channel to supply by the centrifugal force effect with lubricant for cooling and lubrication.

According to an advantageous embodiment of the invention, each pair of rollers to the cylinder drum belonging cylinder drum side half roller and belonging to the drive shaft drive shaft side half roller, wherein the cylinder drum side half roller of a pair of rollers in a cylindrical, in particular partially cylindrical, cylinder drum side recording as bedding and the drive shaft side half roller of a pair of rollers in a cylindrical, in particular part-cylindrical, drive shaft side recording is taken as a bedding. With such pairs of rollers, the forces and torque for driving the cylinder drum can be transmitted in a simple manner. The cylindrical receptacles in which the corresponding half-roll is received and bedded, can be prepared in a simple manner and with little manufacturing effort, which causes in conjunction with the simple and inexpensive to produce half-rolls the follower joint for the entrainment of the cylinder drum low production costs. With the lubrication device according to the invention, in this case, the two half-rollers can also be supplied with lubricant for cooling and lubrication in the area of the bedding in the drive shaft and the cylinder drum during operation of the axial piston machine with a pressure-medium-empty housing.

The axial piston machine according to the invention can be operated only in one direction of rotation, it being sufficient to provide for this direction of rotation one or more driving bodies, which allow a transmission of a driving torque in the desired direction of rotation between the drive shaft and the cylinder drum.

According to an advantageous embodiment of the invention, the axial piston machine is operable in both directions of rotation, wherein for each Direction of rotation in each case at least one driving body is provided for rotationally synchronous entrainment of the cylinder drum. As a result, a transfer of a driving torque in both directions of rotation between the drive shaft and the cylinder drum is achieved in a simple manner.

The axial piston machine according to the invention can be designed as a constant machine with a fixed displacement volume.

In the embodiment of the follower joint as a cone-beam half-roll joint, which can be performed in a simple manner as constant velocity joint, for driving the cylinder drum is also a change in the pivot angle, i. the rotation axes of the drive shaft and the cylinder drum to each other possible, so that with little construction, the execution of the axial piston machine as adjusting with a variable displacement volume is possible.

Figur 1

eine erfindungsgemäße Axialkolbenmaschine in Schrägachsenbauweise in einem Längsschnitt,

Figur 2

einen Ausschnitt der Figur 1 im Bereich des Mitnahmegelenks in einer vergrößerten Darstellung und

Figur 3

einen Schnitt entlang der Linie A-A der Figur 2.

Further advantages and details of the invention will be explained in more detail with reference to the embodiment shown in the schematic figures. This shows

FIG. 1

an axial piston machine according to the invention in a bent-axis design in a longitudinal section,

FIG. 2

a section of the FIG. 1 in the area of the driving joint in an enlarged view and

FIG. 3

a section along the line AA the FIG. 2 ,

The hydrostatic axial piston machine 1 according to the invention designed as a bent axis machine according to FIGS FIGS. 1 to 3 has a housing 2, which consists of a housing pot 2a and a housing cover 2b. In the housing 2, a drive shaft 4 provided with a drive flange 3 is rotatably mounted about a rotation axis R _t by means of bearing devices 5a, 5b. In the illustrated embodiment, the drive flange 3 is integrally formed on the drive shaft 4.

Axially adjacent to the drive flange 3, a cylinder drum 7 is arranged in the housing 2, which is arranged rotatably about an axis of rotation R _z and provided with a plurality Kolbenausnehmungen 8, which are arranged in the illustrated embodiment concentric with the axis of rotation R _{z of} the cylinder drum 7. In each piston recess 8, a piston 10 is arranged longitudinally displaceable.

The rotation axis R _{t of} the drive shaft 4 intersects the rotation axis R _{z of} the cylinder drum 7 at the point of intersection S.

The cylinder drum 7 is provided with a central, concentric with the axis of rotation R _{z of} the cylinder drum 7 arranged longitudinal recess 11 through which the drive shaft 4 extends therethrough. The drive shaft 4 guided through the axial piston machine 1 is mounted on both sides of the cylinder drum 7 by means of the position devices 5a, 5b. For this purpose, the drive shaft 4 is mounted with the drive flange side bearing device 5a in the housing pot 2a and with the cylinder drum side bearing device 5b in the housing cover 2b.

The drive shaft 4 is designed at the drive flange end with a torque transmission means 12, for example a spline, for introducing a drive torque or for tapping a drive output torque. The opposite, cylinder-drum-side end of the drive shaft 4 guided through the axial piston machine 1 ends in the region of the housing cover 2b. In the housing cover 2 b for receiving the drive shaft 4 and the bearing means 5 b a concentric with the axis of rotation R _{t of} the drive shaft 4 arranged bore 14 is formed, which is formed in the illustrated embodiment as a through hole.

The cylinder drum 7 is located to control the supply and discharge of pressure medium in the V formed by the Kolbenausnehmungen 8 and the piston 10 Verdrängerräumen on a control surface 15, which is provided with not shown kidney-shaped control recesses, the inlet port 16 and an outlet port of Form axial piston 1. To connect the displacers V formed by the piston recesses 8 and the pistons 10 with the control recesses, the cylinder drum 7 is provided with a control opening 18 on each piston recess 8.

The axial piston machine 1 of FIG. 1 is designed as an adjusting machine with a variable displacer volume. In the adjustment of the inclination angle α and thus the pivot angle of the rotation axis R _{z of} the cylinder drum 7 with respect to the rotation axis R _{t of} the drive shaft 4 for changing the displacement volume is adjustable. The control surface 15 against which the cylinder drum 7 rests is formed for this purpose on a weighing body 100 which is pivotably arranged in the housing 2 about a pivot axis which lies at the intersection point S of the rotation axis R _{t of} the drive shaft 4 and the rotation axis R _{z of} the cylinder drum 7 and perpendicular to the axes of rotation R _t and R _{z is} arranged.

Depending on the position of the weighing body 100, the inclination angle α of the rotation axis R _{z of} the cylinder drum 7 changes to the rotation axis R _{t of} the drive shaft 4. The cylinder drum 7 can be pivoted to a zero position in which the rotation axis R _{z of} the cylinder drum 7 coaxial with the axis of rotation R _t the drive shaft 4 is. Starting from this zero position, the cylinder drum 7 can be pivoted to one or both sides, so that the axial piston of the FIG. 1 can be executed as unilaterally pivotable or as two-sided pivotable adjusting. A device for pivoting the weighing body 100 and thus the cylinder drum 7 is in the FIG. 1 not shown in detail.

The pistons 10 are each hinged to the drive flange 3. For this purpose, between the respective piston 10 and the drive flange 3 each formed as a spherical joint articulation 20 is formed. The articulation 20 is formed in the illustrated embodiment as a ball joint, which is formed by a ball head 10a of the piston 10 and a spherical cap 3a in the drive flange 3, in which the piston 10 is attached to the ball head 10a.

The pistons 10 each have a collar portion 10b, with which the piston 10 is arranged in the piston recess 8. A piston rod 10c of the piston 10 connects the collar portion 10b with the ball head 10b.

In order to allow a compensating movement of the piston 10 in a rotation of the cylinder drum 7, the collar portion 10 b of the piston 10 with play in the

Piston recess 8 is arranged. The collar portion 10b of the piston 10 may be designed to be spherical. For sealing the piston 10 with respect to the piston recesses 8, a sealing means 21, for example a piston ring, is arranged on the collar portion 10b of the piston 10.

For storage and centering of the cylinder drum 7, a spherical guide 25 is formed between the cylinder drum 7 and the drive shaft 4. The spherical guide 25 is formed by a spherical portion 26 of the drive shaft 4, on which the cylinder drum 7 is arranged with a arranged in the region of the central longitudinal recess 11 hollow spherical portion 27. The center of the sections 26, 27 lies on the intersection point S of the axis of rotation R _{t of} the drive shaft 4 and the axis of rotation R _{z of} the cylinder drum 7.

In order to achieve a driving of the cylinder drum 7 during operation of the axial piston machine 1, a driving joint 30 is arranged between the drive shaft 4 and the cylinder drum 7, which couples the drive shaft 4 and the cylinder drum 7 in the direction of rotation.

The entrainment joint 30 has at least one driving body M1-M4 designed as a sliding body, which is supported in the drive shaft 4 and the cylinder drum 7. Each driving body M1-M4 is for this purpose -as in connection with the FIG. 3 is shown in detail -in each case in a bedding B1 of the drive shaft 4 and a bed B2 of the cylinder drum 7 is added.

The driving body M1-M4 are in the illustrated embodiment in each case as driving body pair P1-P4 with two half-bodies M1 a, M1b - M4a, M4b is formed, which are arranged alternately in the drive shaft 4 and the cylinder drum 7 and abut by means of contact surfaces BF. Each driving body pair P1-P4 has a cylindrical drum-side half body M1a, M2a, M3a, M4a belonging to the cylinder drum 7 and a drive shaft-side half body M1b, M2b, M3b, M4b belonging to the drive shaft 4, wherein the cylindrical drum-side half body M1a, M2a, M3a, M4a of Mitnahmekörperpaars P1-P4 in the bed B2 of the cylinder drum 7 and the drive shaft side half-body M 1 b, M2b, M3b, M4b of Mitnahmekörperpaars P1-P4 in the bedding B1 of the drive shaft 3 is added. The driving joint 30 is formed in the illustrated embodiment as a constant velocity joint, which allows a rotationally synchronous entrainment of the cylinder drum 7 with the drive shaft 4, so that there is a uniform, synchronous rotation of the cylinder drum 7 with the drive shaft 4.

The trained as constant velocity joint driving joint 30 is formed in the illustrated embodiment as a cone beam half-roll joint 31.

The structure of the cone-beam half-roller joint 31, with which the cylinder drum 7 and the drive shaft 4 is rotationally coupled, will be described below with reference to Figures 2 and 3 described in more detail.

The cone-beam half-roll joint 31 is formed by a plurality of roller pairs 50, 51, 52, 53 as driving body pair P1, P2, P3, P4, which are arranged between the drive shaft 4 and a sleeve-shaped driver element 40 connected in a rotationally fixed manner to the cylinder drum 7.

The sleeve-shaped driver element 40 is arranged in the central longitudinal recess 11 of the cylinder drum 7. The driver element 40 is secured to the cylinder drum 7 in the longitudinal direction of the cylinder drum 7 in the axial direction and in the circumferential direction. For axial securing, the driver element 40 rests with an end face against a diameter shoulder 11a of the longitudinal recess 11. The rotation is effected by means of a securing means 45, which is formed in the illustrated embodiment by a arranged between the sleeve-shaped driver element 40 and the cylinder drum 7 connecting pin. The drive shaft 4 guided through the axial piston machine 1 also extends through the sleeve-shaped driver element 40. For this purpose, the inner diameter of the sleeve-shaped driver element 40 is provided with a contour aligned with the longitudinal recess 11 of the cylinder drum 7.

Each of the plurality of roller pairs 50-53 of the cone-beam half-roller joint 31 consists of two and thus a pair of semi-cylindrical half rollers 50a, 50b, 51a, 51b, 52a, 52b, 53a, 53b as half bodies M1a, M1b, M2a, M2b, M3a , M3b, M4a, M4b. The semi-cylindrical half rollers 50a, 50b, 51a, 51b, 52a, 52b, 53a, 53b are each flattened from a substantially to an axis of rotation RR _t , RR _z cylindrical body formed. On the flattened sides, the pairs of half rollers 50a, 50b, 51a, 51b, 52a, 52b, 53a, 53b form planar sliding surfaces GF as contact surfaces BF, on which the two half rollers 50a, 50b, 51a, 51b, 52a , 52b, 53a, 53b of a pair of rollers 50, 51, 52, 53 abut each other to form a surface contact.

The half rollers 50a, 50b, 51a, 51b, 52a, 52b, 53a, 53b and thus the half bodies M1a, M1b, M2a, M2b, M3a, M3b, M4a, M4b are radially spaced within the pitch circle of the pistons 10 and from the axes of rotation R _t , R _z arranged. The driving joint 30 can therefore be arranged space-saving within the pitch circle of the piston 10 and the drive shaft 4 are performed radially within the half-rollers of the cone-beam half-roll joint 31.

Each roller pair 50-53 has a cylindrical drum-side half-roller 50a, 51a, 52a, 53a belonging to the cylinder drum 7 and a drive shaft 4 belonging to the drive shaft side half-roller 50b, 51b, 52b, 53b, which abut the flat sliding surfaces GF and each other stay in contact.

The cylindrical drum-side half roller 50a, 51a, 52a, 53a of the respective roller pair 50-53 are each in a cylindrical, in particular partially cylindrical, cylinder drum side receptacle 55a, 56a, 57a, 58a as bedding B2 and the drive shaft side half roller 50b, 51b, 52b, 53b a pair of rollers 50-53 in a cylindrical, in particular part-cylindrical, drive shaft side receiving 55b, 56b, 57b, 58b taken as bedding B1.

The half rollers 50a, 51a, 52a, 53a, 50b, 51b, 52b, 53b are secured in the respective cylindrical receptacle 55a, 56a, 57a, 58a, 55b, 56b, 57b, 58b in the longitudinal direction of the corresponding axis of rotation.

For this purpose, each half-rollers 50a, 51a, 52a, 53a, 50b, 51b, 52b, 53b are provided in the cylindrical portion with a collar 60 which in a groove 61 of the corresponding receptacle 55a, 56a, 57a, 58a, 55b, 56b , 57b, 58b.

In the FIG. 2 Here, from the roller pair 50 with thick lines, the drive shaft side half roller 50b and with thin lines on the half roller 50b resting cylindrical drum side half-roller 50a shown. Of the roller pair 51, the cylindrical drum-side half roller 51a is shown with thick lines and the thin shaft on the half roller 51a resting on the drive shaft side half roller 51 b. Of the half rollers 50b and 51a are in the sectional plane of the FIG. 2 lying flattened, flat sliding surfaces GF shown.

In the cone-beam half-roll joint 31 are - as in the FIG. 2 are clarified - the rotation axes RR _{t of} the drive shaft side half rollers 50b, 51b, 52b, 53b inclined to the rotation axis R _{t of} the drive shaft 4 by an inclination angle γ. The rotation axes RR _{t of} the drive-shaft-side half-roller 50b, 51b, 52b, 53b intersect the rotation axis R _{t of} the drive shaft 4 at the point of intersection S _t .

The individual rotation axes RR _{t of} the plurality of drive shaft-side half rollers 50b, 51b, 52b, 53b thus form a cone beam about the rotation axis R _{t of} the drive shaft 4 with the point at the intersection S _t .

Correspondingly, the rotational axes RR _{z of} the cylinder-drum-side half rollers 50a, 51a, 52a, 53a are inclined to the rotation axis R _{z of} the cylinder drum 7 by an inclination angle γ. The rotation axes RR _{z of} the cylindrical drum-side half rollers 50a, 51a, 52a, 53a intersect the rotation axis R _{z of} the cylinder drum 7 at the point of intersection S _z . The individual rotation axes RR _{z of} the plurality of cylindrical drum-side half rollers 50a, 51a, 52a, 53a thus form a cone beam about the rotation axis R _{z of} the cylinder drum 7 with the point at the point of intersection S _z .

The inclination angles γ of the rotation axes RR _{z of} the cylinder drum side half rollers 50a, 51a, 52a, 53a to the rotation axis R _{z of} the cylinder drum 7 and the rotation axes RR _{t of} the drive shaft side half rollers 50b, 51b, 52b, 53b to the rotation axis R _{t of} the drive shaft 4 are in magnitude identical. The inclination angles γ of the rotation axes RR _z , RR _{t of} the half rollers of the drive shaft 4 and the cylinder drum 7 to be coupled together are thus the same. In this way it is achieved that in pairs corresponding to the drive shaft 4 axes of rotation RR _t and belonging to the cylinder drum 7 rotational axes RR _z of a pair of rollers forming two half rollers intersect in a plane E, the bisector between the Rotation axis R _{t of} the drive shaft 4 and the rotation axis R _{z of} the cylinder drum 7 corresponds. The in the Level E lying intersections SP, in which pairs the respective belonging to the drive shaft 4 rotation axes RR _t with the cylinder drum 7 associated rotation axis RR _z of a pair of rollers forming two half rollers are in the FIG. 2 clarified. The plane E is thus inclined at half the inclination angle or swivel angle a / 2 with respect to a perpendicular to the axis of rotation R _{t of} the drive shaft 4 plane E1 and a plane perpendicular to the axis of rotation R _{z of} the cylinder drum 7 plane E2. The plane E passes through the intersection S of the axes of rotation R _t , R _z .

The half rollers 50a, 50b, 51a, 51b, 52a, 52b, 53a, 53b of the respective roller pair 50, 51, 52, 53 are arranged in the region of the points of intersection SP of the axes of rotation RR _t , RR _z , whereby at the points of intersection SP two half rollers of the respective roller pair 50-53, the power transmission between the flat sliding surfaces GF takes place for driving the cylinder drum 7.

Due to the position of the intersections SP of the two half rollers of the respective pairs of rollers 50-53 on the plane bisecting plane E results that the vertical radial distances r ₁ , r _{2 of} the intersection points SP to the rotation axis R _{t of} the drive shaft 4 and to the rotation axis R. _z the cylinder drum 7 are equal in magnitude. By the same size, formed by the radial distances r ₁ , r ₂ lever arms of the intersections SP arise equal angular velocities of the drive shaft 4 and the cylinder drum 7, whereby the cone beam half-roller joint 31 forms a constant velocity joint, the exact rotationally synchronous and uniform entrainment and rotation of Cylinder drum 7 allows.

During operation of the axial piston machine 1 during a rotation of the drive shaft 4 takes place at an inclination of the axis of rotation R _{z of} the cylinder drum 7 to the rotation axis R _{t of} the drive shaft 4 with the inclination angle or pivot angle α sliding of the two sliding surfaces GF of the two half rollers of each pair of rollers 50- 53 to each other. In addition, a rotation or rotation of the respective semi-cylindrical half-roller about the respective rotational axis RR _t or RR _{z takes place} in the bedding B1, B2 of the corresponding bedding formed by the cylindrical receptacle 55a, 56a, 57a, 58a, 55b, 56b, 57b, 58b Half roll instead. Due to the inclination of the axes of rotation RR _t , RR _z of each paired half rollers 50a, 50b, 51a, 51b, 52a, 52b, 53a, 53b to each other can be rotated by the corresponding receptacles 55a, 56a, 57a, 58a, 55b, 56b, 57b, 58b align the flat surfaces and thus the sliding surfaces GF of the juxtaposed half rollers to each other.

The in the FIGS. 1 to 3 illustrated axial piston machine 1 is operable in both directions of rotation. In order to achieve a rotationally synchronous entrainment of the cylinder drum 7 in both directions of rotation, at least one driving body M1-M4 or pair of rollers 50-53 is provided for each direction of rotation and thus torque direction of the driving torque for the entrainment of the cylinder drum 7.

In the illustrated embodiment, the driving body M1, M2 and thus the roller pairs 50, 51 serve to entrain the cylinder drum 7 in a rotation of the drive shaft 4 in the counterclockwise direction. In this direction of rotation of the drive shaft 4 51 b of the pairs of rollers 50, 51 forces are transmitted to the flat sliding surfaces GF of the half rollers 50a, 50b and 51 a, which generate a driving torque for driving the cylinder drum 7.

In the illustrated embodiment, the driving body M3, M4 and thus the pairs of rollers 52, 53 serve to entrain the cylinder drum 7 in an opposite rotation of the drive shaft 4 in a clockwise direction. In this case, forces are transmitted to the flat sliding surfaces GF of the half rollers 52a, 52b and 53a, 53b of the roller pairs 52, 53, which generate a driving torque for driving the cylinder drum 7.

In the illustrated embodiment, two pairs of rollers 50, 51 and 52, 53 and thus two driving body M1, M2 or M3, M4 are provided for each rotational direction, wherein the driving body M1, M2 or pairs of rollers 50, 51 for the first direction of rotation and the driving body M3, M4 or roller pairs 52, 53 are distributed uniformly over the circumference for the second direction of rotation. As a result, a radial force balance can be achieved. In the illustrated embodiment with two pairs of rollers per direction of rotation, the pairs of rollers 50, 51 are arranged offset by a rotation angle of 180 ° and the pairs of rollers 52, 53 offset by a rotation angle of 180 °. The roller pairs 50, 51 for the first direction of rotation are offset from the pairs of rollers 52, 53 for the second direction of rotation by a rotation angle of 90 °.

In the illustrated embodiment, the drive shaft side receptacles 55b, 56b, 57b, 58b for the drive shaft side half rollers 50b, 51b, 52b, 53b and thus the bedding B1 of the follower body M1, M2, M3, M4 formed in the drive shaft 4. In the region of the spherical portion 26, the drive shaft 4 is provided for this purpose with a pocket-shaped recess 70, 71, 72, 73, on whose side surfaces in each case a drive shaft-side receptacle 55b, 56b, 57b, 58b and thus a bedding B1 is formed.

In the illustrated embodiment, the cylindrical drum side receptacles 55a, 56a, 57a, 58a for the cylindrical drum side half rollers 50a, 51a, 52a, 53a and thus the bedding B2 of the driving body M1, M2, M3, M4 formed in the sleeve-shaped driving element 40. The sleeve-shaped driver element 40 is provided for this purpose with finger-shaped elevations 41, 42, 43, 44 which extend in the direction of the drive shaft 4 and in which in each case a cylindrical drum-side receptacle 55a, 56a, 57, 58a and thus a bedding B2 is formed. The sleeve-shaped driver element 40 is further provided with the hollow spherical portion 27 of the spherical guide 25.

Each finger-shaped elevation 41, 42, 43, 44 of the driver element 40 engages in an associated pocket-shaped recess 70, 71, 72, 73 of the drive shaft 4 a.

The axial piston machine 1 according to the invention is designed for operation with a pressure-medium-exhausted housing 2. Such an operation means an operation of the axial piston machine 1 in which a low pressure medium level is formed in the housing 2 such that the rotating engine components do not or only slightly dip into pressure medium in order to avoid splashing losses of the rotating engine components during operation of the axial piston machine ,

To allow lubrication and cooling with lubricant on the driving bodies M1-M4 of the driving joint 30, according to the invention a lubricating device 80 is provided for the driving joint 30, by means of the respective driving bodies M1-M4 lubricant, for example hydraulic oil, for cooling and lubrication of the corresponding Mitnahmekörpers M1-M4 of a arranged on the housing 2 of the axial piston machine 1 lubricant port 81 can be fed.

The lubrication device 80 according to the invention is arranged in the drive shaft 4 and has a lubricant channel 82 arranged in the drive shaft 4.

The lubricant passage 81 is formed by a lubricant supply hole 83 arranged in the drive shaft 4, which is connected to the lubricant port 81. Furthermore, the lubricant channel 81 for each driving body M1-M4 of Mitnahmegelenk 30 on a arranged in the drive shaft 4 lubrication hole 84-87. The lubrication holes 84-87 are respectively connected to the lubricant supply bore 83 and extend to the peripheral surface of the drive shaft 4. In the peripheral surface of the drive shaft 4, the lubrication holes 84-87 are each provided with an opening 90-93. The opening 90-93 of the lubricating hole 84-87 are in the illustrated embodiment in the pocket-shaped recess 70, 71, 72, 73 disposed in the peripheral surface of the drive shaft 4 arranged such that upon rotation of the drive shaft 4 via the lubricant supply hole 93 and the lubrication holes 84th Supplied lubricant flows through the centrifugal force occurring on the associated driving body M 1-M4.

The lubrication holes 84-87 are arranged inclined in the illustrated embodiment, each in drive shaft 4 and inclined with the opening 90-93 in the direction of the cylinder drum 7, so that the lubrication holes 84-87 introduced from radially outside, for example by drilling, in the drive shaft 4 can be. The lubrication holes 84-87 can thus be easily made in the drive shaft 4, in which the lubricant supply hole 93 is drilled from radially outward at a desired angle to the bedding B1 of the drive shaft 4 over.

The inclination angle of the lubrication holes 84-87 is preferably selected such that the lubrication holes 84-87 with its longitudinal axis - as in the FIG. 2 is apparent - are directed to the axial center region of the drive shaft side half body M1 b, M2b, M3b, M4b. In the embodiment of the drive shaft side half body M1 b, M2b, M3b, M4b as a semi-cylindrical half roller 50b, 51b, 52b, 53b thus the lubrication holes 84-87 are seen with its longitudinal axis - in the axial longitudinal direction of the half roller 50b, 51b, 52b, 53b - Aligned to the axial center area. The lubrication holes 84-87 and their openings 90-93 are thus directed respectively to the associated follower body M1-M4.

The lubricant exiting through the centrifugal force from the opening 90-93 thus flows directly to the associated driving body M1-M4. The contact surfaces BF of the two half bodies M1a, M1b - M4a, M4b of the respective driving body pair P1-P4 and the surfaces with which the half bodies M1a, M1b - M4a, M4b are arranged in the bedding B1, B2, thus become from the opening 90-93 exiting directly by the centrifugal force lubricant, so that with a small amount of lubricant safe cooling and lubrication of the driving body M1-M4 is achieved.

The lubricant supply bore 83 is formed in the illustrated embodiment as a coaxial with the axis of rotation R _{t of} the drive shaft 4 arranged longitudinal bore in the drive shaft 4.

The trained as a longitudinal bore lubricant supply hole 83 extends in the illustrated embodiment to the cylinder drum side bearing means 5b.

In the area of the cylinder drum side bearing device 5 a, the lubricant supply bore 83 is provided with a supply port 95 which is connected to the lubricant port 81 disposed on the housing 2 of the axial piston engine 1. The feed opening 95 is formed in the illustrated embodiment on the axial end side of the drive shaft 4 and formed by the bore opening of the lubricant supply bore 83. The lubricant supply bore 83 is formed in the illustrated embodiment as a blind bore, which can be introduced from the cylinder drum side end of the drive shaft 4 in the drive shaft 4.

In order to connect the lubricant supply bore 83 with the lubricant port 81 on the housing 2, between the bearing device 5a, the end face of the drive shaft 4 and the housing 2, a lubricant space 96 is formed which communicates with the lubricant port 81. This is in the as Through hole formed bore 14 a cover 97 is arranged, which seals the lubricant chamber 96 to the environment. In the illustrated embodiment, the lubricant port 81 is formed on the lid 97, which is provided for this purpose, for example with a threaded bore 98, to which a lubricant line is connectable.

Cooling and lubrication of the cylinder-drum-side bearing device 5b by means of the lubricant supplied to the lubricant connection 81 is furthermore made possible via the lubricant chamber 96.

The lubrication device 80 according to the invention makes it possible, during operation of the axial piston machine 1 with a pressurized-empty housing 2, to carry the driving body M1-M4 of the driving joint 30 for driving the cylinder drum 7 in a simple manner by means of lubricant supplied to the housing-side lubricant port 81 of the axial piston machine 1 and to lubricate. With the lubrication device 80 according to the invention, in addition, the cylinder drum side bearing device 5b of the drive shaft 4 can be cooled and lubricated by the lubricant supplied to the housing-side lubricant port 81 of the axial piston machine 1.

By the operation of the axial piston machine 1 with a pressure medium emptied housing 2, the churning losses can be reduced, so that in the use of the axial piston engine according to the invention in a vehicle with an internal combustion engine drive, a fuel economy of the engine can be achieved.

The invention is not limited to the illustrated embodiments. The axial piston machine 1 according to the invention can alternatively be designed as a constant machine instead of as an adjusting machine. In a constant machine, the inclination angle α of the rotation axis R _{z of} the cylinder drum 7 with respect to the rotation axis R _{t of} the drive shaft 4 is constant and fixed. The control surface 15 against which the cylinder drum 7 rests can in this case be formed on the housing 2.

It is understood that the driver element 40 can be integrally formed on the cylinder drum 7.

Claims (21)

A hydrostatic axial piston machine (1) in a bent-axis construction with a drive shaft (4) arranged rotatably about a rotation axis (R _t ) within a housing (2) and provided with a drive flange (3) and rotatable within a rotation axis (R _z ) a cylinder (7) is provided with a plurality of Kolbenausnehmungen (8), in each of which a piston (10) is arranged longitudinally displaceable, wherein the piston (10) the drive flange (3) are articulated, and wherein between the drive shaft (4) and the cylinder drum (7) a driving joint (30) for driving the cylinder drum (7) is arranged, wherein the driving joint (30) at least one as a sliding body or as Rolling body formed driving body (M1, M2, M3, M4), which is supported in the drive shaft (4) and the cylinder drum (7), characterized in that a lubricating device (80) for the Mi Taken joint (30) is provided by means of the driving body (M1; M2; M3; M4) lubricant for cooling and lubrication of the driving body (M1, M2, M3, M4) by a on the housing (2) of the axial piston machine (1) arranged lubricant port (81) can be fed. Hydrostatic axial piston machine according to claim 1, characterized in that the lubricating device (80) in the drive shaft (4) is arranged and in the drive shaft (4) arranged lubricant channel (82). Hydrostatic axial piston machine according to claim 2, characterized in that the lubricant channel (82) arranged in the drive shaft (4) lubricant supply bore (83) which is connected to the lubricant port (81), and at least one in the drive shaft (4) arranged lubrication hole ( 84; 85; 86; 87) which is connected to the Schiermittelversorgungsbohrung (83) and which extends to the peripheral surface of the drive shaft (4) and in the peripheral surface with an opening (90; 91; 92; 93) is provided the opening (90; 91; 92; 93) of the lubrication hole (84; 85; 86; 87) is arranged in the circumferential surface such that upon rotation of the drive shaft (4) via the lubricant supply bore (83) and the lubricating bore (84; 85; 86; 87) supplied lubricant by the centrifugal force occurring on the driving body (M1, M2, M3, M4) flows. Hydrostatic axial piston machine according to one of claims 1 to 3, characterized in that the entrainment body (M1; M2; M3; M4) is received in a bedding (B1) of the drive shaft (4) and in a bedding (B2) of the cylinder drum (7) , Hydrostatic axial piston machine according to claim 3 or 4, characterized in that the lubricating bore (84; 85; 86; 87) is directed onto the driving body (M1; M2; M3; M4). Hydrostatic axial piston machine according to one of claims 3 to 5, characterized in that a plurality of circumferentially distributed driving bodies (M1, M2, M3, M4) are provided, wherein for each driving body (M1; M2; M3; M4) a lubricating bore (84 ; 85; 86; 87). Hydrostatic axial piston machine according to one of claims 3 to 6, characterized in that the lubricant supply bore (83) as a coaxial with the axis of rotation (R _t ) of the drive shaft (4) arranged longitudinal bore in the drive shaft (4) is formed. Hydrostatic axial piston machine according to one of claims 3 to 7, characterized in that the lubricant supply bore (83) to a bearing means (5b) extends, by means of which the drive shaft (4) in the housing (2) is rotatably mounted. Hydrostatic axial piston machine according to one of claims 3 to 8, characterized in that the drive shaft (4) in the housing (2) on both sides of the cylinder drum (7) is mounted, wherein the bearing of the drive shaft (4) in the housing (2) a drive flange side bearing device (5a) and a cylinder drum side bearing means (5b), wherein the lubricant supply hole (83) extends to the cylinder drum side bearing means (5b). Hydrostatic axial piston machine according to claim 8 or 9, characterized in that the lubricant supply bore (83) in the region of the bearing device (5b) is provided with a feed opening (95) which is connected to the lubricant connection (81) arranged on the housing (2) of the axial piston machine (1). connected is. Hydrostatic axial piston machine according to claim 10, characterized in that the feed opening (95) is formed on an axial end side of the drive shaft (4). Hydrostatic axial piston machine according to one of claims 8 to 11, characterized in that between the bearing device (5b), the end face of the drive shaft (4) and the housing (2) a lubricant space (96) is formed, which with the lubricant connection (81) in Connection stands. Hydrostatic axial piston machine according to one of claims 1 to 12, characterized in that the entrainment body (M1; M2; M3; M4) as driving body pair (P1; P2; P3; P4) with two half bodies (M1a, M1b, M2a, M2b; M3a, M3b, M4a, M4b), which are arranged alternately in the drive shaft (4) and the cylinder drum (7) and abut against one another by means of contact surfaces (BF), wherein the driving body pair (P1; P2; P3; P4) leads to the cylinder drum (4). M4a) and a drive shaft side half body (M1b; M2b; M3b; M4b) belonging to the drive shaft (4), wherein the cylindrical drum side half body (M1a; M2a; M3a; M4a) of the P4) in a bedding (B2) of the cylinder drum (7) and the drive shaft side half body (M1b; M2b; M3b; M4b) of the driving body pair (P1; P2; P3; P4) in a bedding (B1 ) of the drive shaft (4) is received. Hydrostatic axial piston machine according to one of claims 4 to 13, characterized in that with the lubricating device (80) the half bodies (M1a, M1b, M2a, M2b, M3a, M3b, M4a, M4b) in the region of the contact surfaces (BF) and / or Area of bedding (B1, B2) lubricant is supplied. Hydrostatic axial piston machine according to one of claims 1 to 14, characterized in that the driving pin (30) as a rotationally synchronous driving joint for rotationally synchronous rotation of the cylinder drum (7) and the drive shaft (4) is formed. Hydrostatic axial piston machine according to one of claims 1 to 15, characterized in that the entrainment joint (30) is formed as a cone-beam half-roll joint (31), the at least one pair of rollers (50; 51; 52; 53) as entrainment body pair (P1; P2; P3 P4) having two semi-cylindrical half-rollers (50a, 50b; 51a, 51b; 52a, 52b; 53a, 53b) as a half-body (M1a, M1b, M2a, M2b, M3a, M3b, M4a, M4b), the semi-cylindrical half-rollers (50a, 50b; 51a, 51b; 52a, 52b; 53a, 53b) are flattened to a rotational axis (RRt; RRz) and the half rollers (50a, 50b; 51a, 51b; 52a, 52b; 53a, 53b) abut the flattened sides flat sliding surfaces (GF) form as contact surfaces (BF), where the half rollers (50a, 50b, 51a, 51b, 52a, 52b, 53a, 53b) of the roller pair (50; 51; 52; abut one another on a surface contact. Hydrostatic axial piston machine according to one of claims 1 to 16, characterized in that the driving body (M1; M2; M3; M4), in particular the half rollers (50a, 50b; 51a, 51b; 52a, 52b; 53a, 53b), in radial Direction within the piston (10) and spaced from the axes of rotation (R _t , R _z ) of the drive shaft (4) and the cylinder drum (7) is arranged. A hydrostatic axial piston machine according to claim 16 or 17, characterized in that each roller pair (50; 51; 52; 53) has a cylindrical drum-side half-roller (50a; 51a; 52a; 53a) belonging to the cylinder drum (7) and a drive shaft (4) 51b, 52b, 53b) of a roller pair (50; 51; 52; 53) in a cylindrical, in particular partially cylindrical, cylinder-drum-side receptacle (50b; 51a; 55a, 56a, 57a, 58a) as bedding (B2) and the drive-shaft-side half-roller (50b, 51b, 52b, 53b) of a roller pair (50, 51, 52, 53) in a cylindrical, in particular part-cylindrical, drive shaft-side receptacle (55b, 56b) ; 57b; 58b) is included as bedding (B1). Hydrostatic axial piston machine according to one of claims 1 to 18, characterized in that the axial piston machine (1) is operable in both directions of rotation, wherein for each direction of rotation in each case at least one driving body (M1, M2, M3, M4) for rotationally synchronous entrainment of the cylinder drum (7). is provided. Hydrostatic axial piston machine according to one of claims 1 to 19, characterized in that the axial piston machine (1) is designed as a constant machine with a fixed displacement volume. Hydrostatic axial piston machine according to one of claims 1 to 19, characterized in that the axial piston machine (1) is designed as adjusting with a variable displacer volume, wherein the inclination of the rotation axis (R _z ) of the cylinder drum (7) with respect to the axis of rotation (R _t ) of the Drive shaft (4) is changeable.

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