Axial piston machine with retraction plate for high rotation speed

Abstract

The invention relates to an axial piston machine of the swash plate construction type, having a retraction plate, the first opening of which is penetrated by a respective associated carriage. According to the invention, the hinge section of the carriage deviates from the cylindrical shape in such a way that it has a maximum diameter which is arranged at a distance from the slat section, the hinge section having a diameter which is reduced relative to the maximum diameter between the maximum diameter and the slat section, the hinge section is in contact with the inner circumferential surface of the associated first through-hole in such a way that a minimum distance is produced between the slat section and the spherical outer surface section, the inner circumferential surface of the first through-hole being adapted to the non-cylindrical hinge section of the slide carriage in such a way that the inner circumferential surface of the first through-hole is in contact with the inner circumferential surface of the spherical outer surface section. The inner circumferential surface and the hinge section are in contact with each other at a distance from the maximum diameter of the hinge section in a reference state.

Description

Technical Field

[0001] The invention relates to an axial piston machine according to the preamble of claim 1 . Background Art

[0002] An axial piston machine with a swash plate type of construction is known from US Pat. No. 3,382,793. During suction, the plunger is pulled out of the cylinder bore via the retraction plate. The slide seat at the plunger is supported via an annular surface at the completely flat first end side of the retraction plate. The retraction plate is supported on a retraction ball, which in turn is supported on the cylinder drum via a spring. The retraction plate is designed to be thicker radially on the inside than on the outside. The required rigidity of the retraction plate is thereby achieved, wherein the maximum possible pivoting angle is slightly influenced by the retraction plate being thin on the outside.

[0003] Another comparable retraction plate in an axial piston machine of the swash plate type is known from US Pat. No. 9,856,851 B2.

[0004] A retraction plate of slightly different shape is known from EP 1561031 B1, in which an annular projection is provided on the retraction plate in the region of the retraction ball. This annular projection serves, among other things, to reinforce the retraction plate. Within the scope of the present invention, such an annular projection is not used, because it would require a slide that extends radially further to the outside, contrary to the object setting of the present invention explained below.

[0005] From DE 102020202316 A1 and DE 102015208886 A1, tailored slides are known, in which the rotationally symmetrical articulated sections next to the strip sections are not cylindrical but tailored. Accordingly, the articulated sections have a maximum diameter, wherein the region between the strip sections and the maximum diameter is designed with a smaller diameter. Summary of the invention

[0006] Within the scope of the invention, an axial piston machine with a swash plate design should be obtained which can be operated at high rotational speeds. In this case, the plunger is loaded with large centrifugal forces. Accordingly, the unsupported length, with which the maximally extended plunger protrudes from the cylinder drum, should be particularly small, so that the centrifugal forces generated during operation cause smaller bending moments on the plunger. In addition, the diameter, on which the center point of the ball joint between the slide and the plunger extends, should be particularly small, so that the centrifugal forces acting on the slide are small.

[0007] According to claim 1, it is proposed that: the articulated section of the slide deviates from the cylindrical shape in such a way that it has a maximum diameter, which is arranged at a distance from the strip section, wherein between the maximum diameter and the strip section, the articulated section has a diameter that is reduced relative to the maximum diameter, wherein in a reference state (Bezugszustand), the articulated section is in contact with the inner circumferential surface of the associated first perforation in such a way that a minimum distance is produced between the strip section and the spherical outer surface section, wherein the inner circumferential surface of the first perforation is adapted to the non-cylindrical articulated section of the slide in such a way that the inner circumferential surface and the articulated section are in contact in the reference state at a location away from the maximum diameter of the articulated section.

[0008] The control surface is preferably configured to be flat. The control surface can be arranged at the housing of the axial piston machine in a fixed position. Preferably, a separate swing seat (Schwenkwiege) that can swing relative to the housing is provided, wherein the control surface is arranged at the swing seat. The distance between the first end face and the second end face is preferably continuously variable, wherein the distance is extremely preferably monotonically decreasing from the inside to the outside, wherein there may be an area with a constant distance. The minimum diameter of the first perforation is preferably greater than the maximum diameter of the articulated section. All slides are preferably constructed identically to each other. All first perforations are preferably constructed identically to each other, wherein they are evenly distributed on the circumference of the retraction plate. In the reference state, the annular surface of the slide is particularly against the flat first end face of the retraction plate, wherein the spherical outer surface segment of the retraction ball is against the second perforation of the retraction plate. At the maximum diameter of the articulated section, there may be contact with the inner circumferential surface of the first perforation in the reference state. However, preferably there is a smaller distance to produce a defined contact position, which is away from the maximum diameter.

[0009] Advantageous developments and refinements of the invention are specified in the dependent claims.

[0010] It can be provided that the articulated section of the slide comprises a cylindrical first section, whose diameter is smaller than the maximum diameter of the articulated section, wherein the cylindrical first section is arranged between the strip section and the maximum diameter, wherein the inner circumferential surface of the first perforation comprises a cylindrical second section, wherein in the reference state the cylindrical first and second sections are in contact with each other. Thus, in the fully assembled axial piston machine, the minimum gap size between the cylindrical first and second sections is designed to be very small, wherein there is no concern about contact despite this. Accordingly, the slide can be arranged close to the axis of rotation, thereby minimizing the centrifugal forces acting on the slide.

[0011] It can be provided that the cylindrical second section forms an angle with the first end face, which angle is rounded or chamfered if necessary. Accordingly, the cylindrical first section is arranged directly adjacent to the first end face. Thus, the cylindrical first section is also present radially outside the first perforation despite the fact that the retraction plate has a smaller thickness there.

[0012] It can be provided that the inner circumference of the first aperture is designed to widen in a funnel shape away from the cylindrical second section. This takes into account the maximum diameter of the articulated section. The exact shape of the funnel-shaped widening is not important within the scope of the invention, only that it is ensured that in the reference state the required contact occurs away from the maximum diameter.

[0013] It can be provided that the variable distance between the first and second end faces is designed such that a funnel-shaped widening is present at the radially inner edge of the first perforation, wherein only the cylindrical second section is present at the radially outer edge of the first perforation. The thickness of the retraction plate at the radially outer edge determines the maximum length by which the plunger can protrude from the associated cylinder bore. By means of the proposed design, this length can be minimized and thus also the bending moments caused by centrifugal forces at the plunger can be minimized.

[0014] It can be provided that the axial piston machine is designed in such a way that the reference state can only be reached when at least a part of the axial piston machine is disassembled and / or when the axial piston machine is not put under pressure ready for operation, so that during the predetermined operation of the axial piston machine, there is always at least a certain distance between the slide and the associated first through-hole. A corresponding contact can cause noise and / or wear during operation, which is undesirable.

[0015] It can be provided that: the inner circumferential surface of the second perforation includes a first and a second rotationally symmetrical section, the first and the second sections are directly adjacent to each other, wherein the first rotationally symmetrical section is arranged adjacent to the first end face, wherein the first rotationally symmetrical section is constructed so that it can contact the spherical outer surface section of the retraction ball over the entire circumference, wherein the second rotationally symmetrical section is arranged to have a distance from the spherical outer surface section. The retraction plate is preferably constructed to be thicker in the radially inner part to ensure the required rigidity. Through the above design, it can be achieved that the contact between the retraction plate and the retraction ball is still carried out very close to the first end face, thereby avoiding undesirable tilting moments acting on the retraction plate.

[0016] It can be provided that the rotationally symmetrical second section is spherical in design, wherein the corresponding spherical radius is greater than the spherical radius of the spherical outer surface section of the retraction ball. As a result, a desired distance between the surfaces can be reliably achieved.

[0017] It can be provided that the rotationally symmetrical first section is designed as a cone. As a result, a defined linear contact is formed over the entire circumference of the retraction ball. The distance between the first end face and the contact preferably has a minor dimension that is not zero.

[0018] It can be provided that the rotationally symmetrical second section is designed as a cone, wherein the angle of inclination between the center axis of the rotationally symmetrical first section and the second perforation is greater than a similar angle of inclination at the rotationally symmetrical second section. The production of the second perforation can thus be simplified in that the ideal spherical shape of the rotationally symmetrical second section is approximated by the cone.

[0019] It can be provided that the spherical outer surface segment extends as far as the end of the retraction ball facing the cylinder drum, so that the retraction plate can be swiveled beyond said end, wherein the variable distance between the first and second end faces of the retraction plate is designed such that in the swiveled position of the retraction plate, a gap with a constant width is produced between the second end face of the retraction plate and the cylinder drum. The swiveling position preferably corresponds to the maximally prescribed swiveling angle of the swivel seat during operation. It goes without saying that the swivel seat can be swiveled further outwards until the retraction plate contacts the cylinder drum. The end stop that is preferably present for the swivel seat is very preferably set in such a way that the desired swiveling position is obtained as the end position. With this design, even at the maximum displacement volume In the case of the piston, the piston only protrudes a little from the cylinder drum, so that the centrifugal force explained at the beginning causes a small bending moment at the piston.

[0020] It goes without saying that the features mentioned above and the features still to be explained below can be used not only in the respectively specified combination but also in other combinations or alone without departing from the scope of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] The present invention is described in more detail below with the aid of the accompanying drawings, wherein:

[0022] Figure 1 shows a longitudinal section of an axial piston machine according to the invention;

[0023] Figure 2 shows a longitudinal section of a cylinder drum with a retraction plate according to the invention;

[0024] Figure 3 Shown according to Figure 2 a perspective cross-sectional view of the retraction plate; and

[0025] Figure 4 Shown with Figure 2 A similar cross-section is an enlarged section in the area of ​​the retraction ball. DETAILED DESCRIPTION

[0026] Figure 1 A longitudinal section of an axial piston machine 10 according to the present invention is shown. The axial piston machine 10 comprises a housing 12, in which a drive shaft 14 is rotatably mounted relative to an axis of rotation 11. Two corresponding rotary bearings 15 are designed as tapered roller bearings. Inside the housing 12, the drive shaft 14 is surrounded by a cylinder drum 20 and is connected to the cylinder drum for rotational driving via a spline shaft transmission (Keilwellenverzahnung). A plurality of plungers 22 are accommodated in the cylinder drum 20 in a linearly movable manner. Each plunger 22, together with the cylinder drum 20, defines a cylinder chamber 21, the volume of which changes periodically when the cylinder drum 20 rotates.

[0027] exist Figure 1 At the right end of the cylinder drum 20, the cylinder drum 20 rests on a separate distribution plate 16, which is firmly connected to the housing 12. The distribution plate 16 has two kidney-shaped control holes, which are each permanently connected to the respective associated working interface 13. The cylinder chambers 21 each have an opening, which can be respectively coincident with the kidney-shaped control holes in such a way that the rotation of the cylinder drum 20 is accompanied by a fluid flow between the two working interfaces 13. The corresponding pressurized fluid is preferably a liquid, and very preferably a hydraulic oil.

[0028] On the side of the cylinder drum 20 facing away from the distributor plate 16, a separate pivoting table 70 is arranged, which can be pivoted relative to the housing 12 about a pivot axis 71. The corresponding pivoting movement is caused by the servo cylinder. Figure 1 The servo cylinder is not visible in the drawing. In the present case, the swivel axis 71 intersects the rotation axis 11 at a right angle. However, it is also conceivable that the swivel axis 71 intersects the rotation axis 11 at a distance. The swivel seat 70 has a flat control surface 72, the inclination of which relative to the rotation axis 11 determines the displacement volume of the axial piston machine 10.

[0029] Each plunger 22 is connected to the associated slide 30 via a ball joint 23, wherein the slide 30 slidably rests against the control surface 72. A hydrostatic pressure field is provided between the slide 30 and the control surface 72, to which the associated cylinder chamber 21 provides pressure.

[0030] In order to pull the plunger 22 out of the cylinder drum 20 during suction, a separate retraction plate 50 is provided, which is supported on the cylinder drum 20 via a separate retraction ball 80. When the swivel seat 70 is adjusted, an axial relative movement can occur between the retraction ball 80 and the cylinder drum 20, so these components are constructed separately from each other.

[0031] Figure 21 shows a longitudinal section of a cylinder drum 20 with a retraction plate 50 according to the invention. A position of the retraction plate 50 is shown, in which the swivel seat ( Figure 1 The number 70 in FIG. 7 represents the maximum swivel angle that occurs during operation. In order to achieve the desired high speed stability, Figure 2 The lower plunger 22 in the cylinder drum 20 should protrude as little as possible from the cylinder drum 20, because the corresponding protrusion length determines the bending moment acting on the plunger 22 by the centrifugal force generated during operation. Therefore, the slide 30 on the opposite side of the rotation axis 11 is inserted into the cylinder bore 26, in which the relevant plunger 22 runs. Therefore, the maximum diameter 36 of the articulation area 34 of the slide 30 is preferably smaller than the diameter of the cylinder bore 26. In addition, due to the inclination of the slide 30, a cylindrical first section 37 is provided at the articulation section 34 of the slide 30, whose diameter is smaller than the maximum diameter 36, in order to avoid collisions between the cylinder bore 26 and the slide 30.

[0032] The retraction ball 80 has a spherical outer surface segment 81, the center of which preferably coincides with the rotation axis 11. The spherical outer surface segment 81 extends along the direction of the rotation axis 11 over the entire length of the retraction ball 80. The two ends of the spherical outer surface segment 81 pointing in the direction of the rotation axis 11 are configured so that the central second through hole 54 of the retraction plate 50 can move over the ends of the spherical outer surface segment 81, such as in Figure 2 This is the case shown above. This allows a large axial displacement of the retraction ball 80. Within the scope of this displacement, the retraction ball 80 is supported on the cylinder drum 20 in the direction of the rotation axis 11, for example, by means of a press pin 83 and a helical spring 82 known from EP 1604113 B1. It is also conceivable to install a disc spring in the space marked with the number 84 between the retraction ball 80 and the cylinder drum 20, in particular when only a small axial displacement of the retraction ball 80 is required. The retraction ball 80 is preferably designed in the shape of a pot, wherein the retraction ball surrounds a cylindrical projection on the cylinder drum 20, which points in the direction of the rotation axis 11.

[0033] The ball diameter of the spherical outer surface segment 81 is selected to be as large as possible, wherein collisions between the retraction ball 80 and the plunger 22 are nevertheless reliably excluded. At the same time, the plunger 22 should be arranged as close as possible to the axis of rotation 11 in order to minimize the centrifugal forces generated during operation. The retraction plate 50 according to the invention is designed in this way so that the above-mentioned contradictory requirements can be met as well as possible.

[0034] The rotationally symmetrical outer circumferential surface 32 of the slide 30 comprises a strip section 33 and an articulation section 34. The articulation section 34 forms the spherical seat 31 of the ball joint 23 in the interior. The outer diameter of the strip section 33 is greater than the maximum diameter 36 of the articulation section 34. Therefore, an annular surface 35 is formed at the transition between the strip section 33 and the articulation section 34, which is preferably designed to be flat and perpendicular to the symmetry axis of the rotationally symmetrical body of the slide 30. The slide 30 rests with the annular surface 35 on the flat first end face 51 of the retraction plate 50. The strip section 33 is preferably designed to be cylindrical.

[0035] No contour is provided on the retracting plate 50 that protrudes from the flat first end face 51 toward the swivel seat 70. In particular, no annular reinforcement protrusion is arranged around the central second through hole 54. This design allows the strip section 33 to be very close to the spherical outer surface section 81, more precisely, when, for example, Figure 2 In contrast to the illustration in FIG. , when the displacement volume is set to zero. In this state, the articulated section 54 of the slide is arranged in the retraction plate 50 very close to the radial inner edge of the associated first through-hole 53 .

[0036] It should be noted here that the diameter of the first through-hole 53 is significantly larger than the maximum diameter 36 of the articulated section 34. Therefore, the slide 30 can move in the first through-hole 53 to compensate for the distance between the slide 30 and the axis of rotation 11, which changes during the rotation of the cylinder drum 20 and is parallel to the control surface ( Figure 1 When the displacement volume is zero, the distance is constant and minimum.

[0037] In particular, within the scope of the invention, the cross-sectional shape of the first aperture 53 is adapted to the non-cylindrical shape of the respectively associated joint section 34 in order to achieve a minimum distance between the strip section 33 and the spherical outer surface section 81 that is as small as possible.

[0038] In the present retraction plate 50, the required rigidity is achieved in that the second end face 52 remote from the first end face 51 is not flat. Instead, the distance between the first end face 51 and the second end face 52 or the thickness of the retraction plate 50 is significantly greater radially inwardly than radially outwardly. The corresponding thickness curve is selected so that Figure 2 At the maximum displacement volume shown in , a gap 25 with a constant width is produced between the retraction plate 50 and the cylinder drum 20. In any case, the corresponding end side 27 of the cylinder drum 20 is configured flat around the plunger 22 and perpendicular to the rotation axis 11 so that the plunger 22 is supported as well as possible by the respective cylinder bore 26.

[0039] At the radially outer edge, the retraction plate 70 has a region of constant thickness, wherein the cylinder drum 20 is adjusted so that the width of the gap 25 is constant.

[0040] Figure 3 Shown according to Figure 2 50. The corresponding section plane contains the central axis 59, about which the second through-holes 54 are designed rotationally symmetrically. The first end face 51 is designed flat and perpendicular to the central axis 59. In the present case, nine first through-holes 53 are arranged around the central axis 59. These first through-holes are designed identically to one another, wherein they are evenly distributed on a common pitch circle, the center point of which coincides with the central axis 59.

[0041] Each first perforation 53 is rotationally symmetrically constructed with a constant cross-sectional shape, wherein due to the variable thickness of the retraction plate 50, the cross-sectional shape does not exist completely on the radial outside. The cross-sectional shape is composed of a cylindrical second section 57, which is arranged adjacent to the first end face 51. A funnel-shaped expansion portion 58 is connected to the cylindrical second section, which is constructed so large that when the relevant slide abuts against the cylindrical second section 57, the slide does not abut against the expansion portion. It should be noted here that during the operation of the axial piston machine, this reference state preferably does not occur. However, for a single slide, this reference state can be easily induced in the following way: in Figure 2 In the case of the structural assembly shown in , the displacement volume is set to zero, wherein the retraction plate 50 is radially moved relative to the rotation axis. Due to the variable thickness of the retraction plate 50, the funnel-shaped expansion 58 is only present at the radial inner edge of the first perforation 53, wherein it is precisely at the radial inner edge of the first perforation that the funnel-shaped expansion is required.

[0042] In addition, Figure 3 It can also be seen in FIG. 5 that the central second aperture 54 comprises a rotationally symmetrical first and second section 61 ; 62 , which in the present case are separated from one another by an edge.

[0043] Figure 4 Shown with Figure 2 A similar cross-sectional view is an enlarged section in the area of ​​the retraction ball 80. Figure 2 In contrast, the section plane is slightly twisted about the rotation axis, so that the slide 30 does not fall into the section plane. The second through hole 54 of the retraction plate 50 includes a first and a second rotationally symmetrical section 61; 62, the first and second sections being located at the center axis ( Figure 359 in the figure). The contact between the retraction plate 50 and the spherical outer surface segment 81 occurs in the rotationally symmetrical first segment 61, which is adjacent to the first end face 51. The rotationally symmetrical first segment 61 is configured as a cone, so that linear contact is produced over the entire circumference of the retraction ball 80. Currently, the rotationally symmetrical second segment 62 is configured as a sphere, wherein the corresponding spherical radius is configured to be larger than the spherical radius of the spherical outer surface segment 81 by a predetermined gap size. However, the corresponding spherical shape can also be approximated by a cone without causing any disadvantages worth mentioning.

[0044] This shaping makes it possible to have a small but reliably non-zero distance between the linear contact and the first end face 51. Thus, the interfering tilting moments acting on the retraction plate are minimized, wherein despite this, there is no need to worry about excessive wear at the inner circumference 56 of the second perforation 54.

[0045] Reference Mark:

[0046] 10Axial piston machine

[0047] 11 Rotation axis

[0048] 12 Shell

[0049] 13 working interface

[0050] 14 Drive shaft

[0051] 15 Rotary bearing

[0052] 16 distribution board

[0053] 20 cylinder roller

[0054] 21 Cylinder room

[0055] 22 Plunger

[0056] 23 Ball joint

[0057] 24 ball head

[0058] 25 Clearance between retract plate and cylinder roller

[0059] 26 cylinder bores

[0060] 27 End side of cylinder drum

[0061] 30 Slide

[0062] 31 Ball Seat

[0063] 32 Outer circumference of the slide

[0064] 33 Slat Section

[0065] 34 articulated sections

[0066] 35 Torus

[0067] 36 Maximum diameter of the articulated section

[0068] 37 cylindrical first section

[0069] 50 retractable plate

[0070] 51 first end surface

[0071] 52 second end surface

[0072] 53 First Punch

[0073] 54 Second Punch

[0074] 55 Inner circumferential surface of the first perforation

[0075] 56 The inner circumference of the second perforation

[0076] 57 cylindrical second section

[0077] 58 Funnel-shaped extension

[0078] 59 Central axis of the first perforation

[0079] 61 Rotationally symmetrical first section

[0080] 62 Rotationally symmetrical second section

[0081] 63 Corner between the first through hole and the first end surface

[0082] 64 Corner between the second through hole and the first end surface

[0083] 70 Swing Turntable

[0084] 71 Swing axis

[0085] 72 Control Surface

[0086] 80 Retraction Ball

[0087] 81 Spherical outer surface segment

[0088] 82 coil spring

[0089] 83 Press Pin

[0090] 84 Space for disc springs.

Claims

1. An axial piston machine (10) comprising a cylinder drum (20) rotatable relative to an axis of rotation (11), wherein a plurality of pistons (22) are accommodated in the cylinder drum in a linearly movable manner, so that the pistons and the cylinder drum (20) respectively define an associated cylinder chamber (21) with a variable volume, wherein each piston (22) is connected to a slide (30) via a spherical joint (23), wherein the slide (30) is slidably attached to a control surface (72). wherein the control surface (72) can be arranged at an angle other than 90° relative to the rotation axis, wherein a retraction plate (50) is provided, the retraction plate having a first through-hole (53) for each slide seat (30), wherein the retraction plate (50) has a flat first end surface (51), wherein the outer circumferential surface (32) of the slide seat (30) is rotationally symmetrically configured, wherein the outer circumferential surface is composed of a strip section (33) and an articulated section (34), wherein the diameter of the strip section (33) is larger than the diameter of the articulated section ( The invention relates to a method for manufacturing a retractable plate (50) having a maximum diameter (36) of the retractable plate (50) and a plurality of retractable plates (51). The method comprises: firstly, a retractable plate (50) and a retractable plate having a maximum diameter (36) of the retractable plate (50), wherein the retractable plate (50) has a maximum diameter (36) of the retractable plate (50), so that an annular surface (35) is generated at the transition between the strip section (33) and the hinge section (34), the annular surface abutting against the first end face (51), wherein a retractable ball (80) is arranged, the retractable ball having a spherical outer surface section (81), wherein the retractable plate (50) has a central second through-hole (54), the inner circumferential surface (56) of the second through-hole abutting against the spherical outer surface section (81), wherein the inner circumferential surface is shaped like the flat first end face. The invention relates to a cylinder drum (20) having a retraction ball (80) and a control surface (72) formed at an angle (64), which is rounded or chamfered if necessary, wherein the retraction ball (80) is supported on the cylinder drum (20) in the direction of the rotation axis (11) in such a way that the slide (30) can be pressed onto the control surface (72) by the retraction plate (50), wherein the retraction plate (50) has a second end surface (52) facing away from the first end surface (51), the second end surface is designed rotationally symmetrically, wherein the distance between the first and second end surfaces (52; 52) is smaller radially on the outside than on the inside, It is characterized in that The articulated section (34) of the slide (30) deviates from the cylindrical shape in such a way that it has a maximum diameter (36) which is arranged at a distance from the strip section (33), wherein between the maximum diameter (36) and the strip section (33), the articulated section has a diameter which is reduced relative to the maximum diameter (36), wherein in a reference state the articulated section (34) is in contact with the inner circumferential surface (55) of the associated first perforation (53) in such a way that a minimum distance is produced between the strip section (33) and the spherical outer surface section (81), wherein the inner circumferential surface (55) of the first perforation (53) is adapted to the non-cylindrical articulated section (34) of the slide (30) in such a way that the inner circumferential surface (55) and the articulated section (34) are in contact in a reference state at a location away from the maximum diameter (36) of the articulated section (34).

2. The axial piston machine (10) according to claim 1, The articulated section (34) of the slide (30) comprises a cylindrical first section (37) whose diameter is smaller than a maximum diameter (36) of the articulated section (34), wherein: A cylindrical first section (37) is arranged between the strip section (33) and the maximum diameter (36), wherein the inner circumferential surface (55) of the first aperture (53) comprises a cylindrical second section (57), wherein in a reference state the cylindrical first and second sections (37; 57) are in contact with each other.

3. The axial piston machine (10) according to claim 2, The cylindrical second section (57) forms a corner (63) with the first end face (51), which corner is rounded or chamfered if necessary.

4. The axial piston machine (10) according to claim 2 or 3, The inner circumferential surface (56) of the first aperture (53) is designed to widen in a funnel-shaped manner (58) away from the cylindrical second section (57).

5. The axial piston segment (10) according to claim 4, The variable distance between the first and second end faces (51; 52) is designed such that a funnel-shaped expansion portion (58) is present at the radial inner edge of the first perforation (53), wherein only a cylindrical second section (57) is present at the radial outer edge of the first perforation (53).

6. The axial piston machine (10) according to any one of the preceding claims, The axial piston machine (10) is designed in such a way that a reference state can only be reached when at least a part of the axial piston machine (10) is disassembled and / or when the axial piston machine (10) is placed under pressure without being ready for operation, so that during the specified operation of the axial piston machine (10), there is always at least a certain distance between the slide (30) and the associated first aperture (51).

7. The axial piston machine (10) according to any one of the preceding claims, The inner circumferential surface (56) of the second perforation (54) includes a first and a second rotationally symmetrical segment (61; 62), which are directly adjacent to each other, wherein the rotationally symmetrical first segment (61) is arranged adjacent to the first end face (51), wherein the rotationally symmetrical first segment is constructed so that it can contact the spherical outer surface segment (81) of the retraction ball (80) over the entire circumference, and wherein the rotationally symmetrical second segment (62) is arranged to have a distance from the spherical outer surface segment (81).

8. The axial piston machine (10) according to claim 7, The rotationally symmetrical second section (62) is spherical in design, wherein the corresponding spherical radius is greater than the spherical radius of the spherical outer surface section (81) of the retraction ball (80).

9. The axial piston machine (10) according to claim 7 or 8, The rotationally symmetrical first section (61) is designed to be conical.

10. The axial piston machine (10) according to claim 9, The rotationally symmetrical second section (62) is designed as a cone, wherein the inclination angle between the rotationally symmetrical first section (61) and the center axis of the second aperture (52) is greater than a similar inclination angle at the rotationally symmetrical second section (62).

11. An axial piston machine according to any one of the preceding claims, The spherical outer surface segment (81) extends to the end of the retraction ball (80) facing the cylinder drum (20), so that the retraction plate (50) can be swung over the end, wherein the variable distance between the first and second end faces (51; 52) of the retraction plate (50) is designed so that in the swung position of the retraction plate (50), a gap (25) with a constant width is generated between the second end face (52) of the retraction plate (50) and the cylinder drum (20).

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