JPS6310304B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The invention relates to a variable displacement axial piston machine of the type defined in the preamble of claim 1. In previously known machines of this type, the component carrying the valve-acting surface supporting the cylinder drum is provided with a cylindrical sliding surface on its rear side and with which a corresponding hollow cylindrical surface in the casing. is supported by Channels for supplying and draining liquid to and from the cylinder drum open simultaneously into these cylindrical surfaces. This requires that these surfaces overlap each other tightly to prevent leakage. Producing these cylindrical surfaces that correspond exactly to each other requires high production costs. This is a disadvantage. The central axes of curvature of these cylindrical surfaces pass through the intersection of the drive shaft axis and the cylinder drum rotation axis in known machines of this type. This arrangement of the center axis of curvature is important because the piston must have sufficient space for stroke movement within the cylinder when the cylinder drum is swiveled to its maximum in order to obtain maximum piston stroke distance. As a result, when the cylinder drum is reversely rotated to a small rotation angle, the distance between the piston end surface and the cylinder end surface at the top dead center position gradually increases as the rotation angle decreases, and therefore the clearance volume increases, Even within this clearance volume, liquid is expanded or compressed when the pressure inside the cylinder changes. Since especially axial piston motors of this type are often operated at high pressure and with the cylinder drum reversely swiveled, the resulting compression losses lead to a significant loss in efficiency. This is also a disadvantage.

The object of the invention is to eliminate the disadvantages of the known machines of the above-mentioned type and to construct the machine in such a way that it does not have corresponding cylindrical guide surfaces, which are difficult to manufacture, and furthermore the clearance volume in the cylinder is as small as possible. There is a particular thing.

This object was achieved by the present invention as follows.
That is, the component with the valve-acting surface is connected to the second component via one joint, which has an axis perpendicular to the plane containing the axis of the cylinder drum and the axis of the drive shaft. The second component is supported on a guide part of the casing and is movable linearly within the casing.

In this regard, first of all, in order to reduce the clearance volume in the cylinder in a rotating casing type drive flange type axial piston pump with variable discharge volume, the rotation axis is set at the intersection of the drive flange shaft axis and the cylinder drum rotation axis. It is well known that external
2102000 and 2105119). In these machines of the rotating casing type, the purpose of reducing harmful clearance volumes is satisfactorily fulfilled. However, the expert also recognizes this solution of the above-mentioned axial piston machine in the form of a pivoting casing as claimed in claim 1 of the invention.
It was considered that it would be impossible to convert this to a rotating carriage-type machine of the type described in the premise concept section of this section. That is, if the center axes of curvature of the corresponding cylindrical surfaces in the rotating carriage type machine are located adjacent to the intersection of the drive shaft axis and the cylinder drum rotation axis, similar to the above-described configuration of the rotating casing type machine, no adjustment is required. This results in a machine in which it is not possible to perform a movement, since in such a swiveling carriage machine the central axis of curvature always has the same relative position to the swivel carriage and thereby also This is because the valve action surface is always perpendicular to the plane containing the central axis of curvature. Moreover, the cylinder drum must rest on this valve-acting surface, but the axis of rotation of the cylinder drum no longer includes the central axis of curvature in this construction. Experts were therefore first forced to confirm that such a structure was not practicable. The addition of further features to achieve guidance for the casing on one side and alignment of the valving surface to the intersection of the cylinder drum rotational axis and the drive shaft rotational axis on the other side requires additional considerations. did. This requires a joint arrangement, which has various embodiments.

The object of the invention can therefore be achieved according to the invention in the following way: the component occupying the position of the previously known swiveling carriage consists of two parts, the valve-acting surface being The carrying member is tiltable relative to the guide member about one axis, such that this axis is perpendicular to the cylinder drum axis and perpendicular to the plane containing the cylinder drum axis and the drive shaft axis. That's what I did. In this case, it is no longer necessary to support the guide member on a cylindrical surface, but instead a flat cylindrical surface and a cylindrical counterpart surface, which can be produced significantly more easily and at a lower cost on ordinary machine tools, are provided. This has the advantage of being able to be supported on a surface. This flat surface can be perpendicular to the drive shaft axis or inclined at a slight angle to the drive shaft axis, the magnitude of which is determined by the piston diameter versus the articulation of the piston within the drive flange. Depends on the ratio of the spacing of the piston end face from the point, which defines the required spacing of the cylinder end face, to the center point of the spherical head of the piston rod, where the piston end face edge is supported in the drive flange. This is because it moves on an arc centered on . The guide member can be supported against a flat surface via a hydraulic pressure cushion which is supplied with pressure in a passage in the valve-acting surface. However, in this case it must be taken into account that this pressure is not proportional to the contact force of the guide member against the support surface.
This is because this supporting force is dependent not only on the hydraulic pressure but also on the swivel angle of the cylinder drum.
Therefore, in a hydraulic pressure cushion in a sliding shoe of a type of swashplate machine, the pressure in the cushion is always related to the pressure in front of the piston end face, regardless of the inclination between the piston axis and the tiltable swashplate. A similar situation arises. However, due to the additional guide elements, especially hydraulic adjustment mechanisms, for adjusting the position of the linear carriage in the machine according to the invention, despite the lack of proportionality between the supporting force and the hydraulic pressure,
Good results can be obtained.

Such linearly movable guide members or linear carriages are suitable for use in previously known swivel carriage machines, in which the adjusting piston must be provided with lateral guide pins which pivotably engage into the swivel carriage. It is possible to connect the adjusting piston, which is movable in the adjusting cylinder, much more easily than would otherwise be the case. The guide element can be a sliding shoe which is pivotably connected to the component carrying the valve-acting surface, or it can be a simple sliding shoe which is mounted on the valve-acting surface component, for example in its round groove, and abuts against the casing. It can be a roll. However, the guide member of the linear carriage can also be supported on the casing by means of guides such as rollers. In a further embodiment, the component which replaces the carriage can also be suspended in the housing via a correspondingly long parallelogram linkage.

Various embodiments are also possible for the construction of the joint between the part with the valve-acting surface and the linear carriage guide supported on the housing, for example as a knife-edge bearing or a roller bearing. Can be done. It should always be noted that in special cases it is possible to suffice with a purely compressive support, or if necessary additional interlocking elements or components with valve-acting surfaces are required. A complete meshing engagement is required to prevent the guide member from separating from the guide member. For example, in the case of a roller bearing, holes are opened in the pressing surface and, if necessary, a pressure cushion is provided surrounding the openings of these holes.
These holes can then be connected to channels in the valve area, so that the joint can be relieved hydraulically. The joint between the component with the valve-acting surface and the guide element can also be designed as a spherical joint. Such an arrangement is advantageous, in particular in that it provides a degree of freedom for adjusting the valve action surface relative to the cylinder drum and avoids jamming. In order to balance the pressing forces occurring on the valve surface, pressure chambers can optionally be provided which generate corresponding balancing forces.

It is not necessary to support the guide element directly on the casing or on a casing element, such as a casing cover, but it is also possible in this way to generate forces in other ways, for example in that the guide element slides on a rod fixed in the casing. It is possible as long as you can control it. Such a rod can at the same time be designed as an adjusting piston or an adjusting spindle.

Due to the deeper penetration of the piston during small swivel angles, the kinematic system for entraining the cylinder drum either directly by the piston rod or indirectly by the piston rod via the respective piston skirt is also improved. be done.

Various embodiments are possible for supplying and discharging working fluid to the valve surface. In suitable embodiments, the supply can take place through the joint. However, the supply can be carried out on both sides of the direction of movement of the linear carriage, with conduits being optionally telescopically telescopically telescopically constructed on each side and optionally pivotably supported at both ends. You can also place . The part carrying the valve actuating surface faces a flat surface of the casing by means of flat surfaces on both sides, and these flat surfaces of the casing each correspond to the rotational axis of the cylinder drum relative to the axis of rotation of the drive shaft. perpendicular to the pivot axis of motion, and the supply and discharge of liquid to the valve-acting surface are carried out respectively through one of these two sides of the component carrying the valve-acting surface, optionally with a hydraulic pressure. A very advantageous liquid guiding occurs if the action takes place via a sealing element which in each case contacts the corresponding component. In order to balance the side pressures, the pressure balancing cushions can each be supplied with pressure from the other side.

Various embodiments are also possible for the guidance of the cylinder drum. The cylinder drum is guided, as is known for rotating carriage machines, on a central pin which, by means of a spherical joint on the axis of rotation of the drive flange, forms at least approximately the spherical shape of the piston rod. Suitably, it is guided in the plane of arrangement of the head. (By shifting the spherical center point of the center pin spherical head out of the plane of arrangement of the spherical head of the piston rod, certain effects can be obtained with respect to the generated return force as well as with respect to the size of the clearance volume.) However, In a suitable embodiment of the invention, the component with the valve-acting surface is also aligned with the center point of the pivot movement of the cylinder drum axis of rotation and for this purpose the central pin is aligned with the component with the valve-acting surface. It is also possible to extend into the component. If the guide member rests on a flat surface or is suspended by a parallelogram linkage, changing the cylinder drum swivel angle will cause the component carrying the valve-acting surface and the drive flange to The interval between changes. For this purpose, either the central pin is mounted vertically displaceably in the component with the valve-acting surface, or the component with the valve-acting surface is guided telescopically in the central pin. must be firmly connected. In the latter case, it is expedient for this element to be connected at the same time to the joint between the component carrying the valve-acting surface and the guide element, or to that element.

The joint connecting the component with the valve-acting surface to the guide element is suitably arranged in such a way that the joint axis intersects the axis of rotation of the cylinder drum. However, it is also possible to arrange the joint axis laterally offset relative to the cylinder drum axis. This creates forces that may serve to balance the adjustment forces in some circumstances.

If the supply and discharge of liquid is to take place in the housing through the supporting surface of the linear carriage in a known manner, an arcuate coupling channel is connected in a telescopic manner to a component having a valve-acting surface. and the guide element, the center point of the circular arc being in each case on the joint axis. However, with such an arrangement additional sealing points are required and pressure-related forces are generated between the component with the valve-acting surface and the guide element.

The joint axis between the component with the valve-acting surface and the guide element is therefore arranged parallel to the pivot axis of the cylinder drum.

If the guide element rests on a flat surface, the linear movement allows the adjusting cylinder to be integrated directly into the guide element, with the piston resting directly on the housing. The liquid can be supplied through the piston.
If flexibility or adjustability is provided to compensate for any manufacturing tolerances, wear or thermal expansion, the piston can be mounted directly in the housing. Since the adjustment force is not only dependent on the working pressure but also on the swiveling position, in order to obtain a symmetrical arrangement,
Two adjusting cylinders are arranged on the side of the guide member in the direction of rotation of the cylinder drum, and one adjusting cylinder on the opposite side is arranged in the central plane, so that large forces are exerted by the two adjusting cylinders. It is appropriate to make it acceptable.

If a spring is used to generate the basic contact force between the cylinder drum and the valve action surface and is supported on a central pin, the spring must have very soft properties; This is because the cylinder drum moves relative to the center pin when changing the swing angle. If the guide pin, which telescopes into the central pin, is connected with the component carrying the valve-acting surface with a stop, a pressure spring is clamped between this pin and the cylinder drum. is appropriate.

Suitably, this pin is arranged immovably in the component having the valve-acting surface. The central pin bearing the cylinder drum rotates together with the cylinder drum (in this case a relative movement occurs with respect to the pin which is mounted immovably in the component defining the valve actuation surface); or Is it non-rotatably guided on this other pin?
There are design issues in each case.

The invention will now be described in detail with reference to the accompanying drawings.

A drive shaft 2 is supported in a casing 1 by rolling bearings 3 and 4. The drive flange 5 is constructed integrally with the drive shaft 2. Drive flange 5
A spherical recess is cut in the interior, in which the spherical head 6 of the piston rod 7 is seated. The piston rod 7 is movably connected to the piston 8 via a joint, such as a ball joint, in order to avoid tension between the drive flange 5, cylinder 9 and cylinder drum 10. The piston 8 is movable in a cylinder 9 arranged in a cylinder drum 10 parallel to the axis of the cylinder drum. The cylinder drum 10 is supported on a center pin 11 which is supported with a spherical head 12 in the center point of the drive flange 5.

The cylinder drum 10 is in contact with the valve action surface 13 of the valve action surface constituting member 14 at its end surface. A further pin 15 is attached to this valve-acting surface component 14, which pin 15 enters the longitudinal bore of the central pin 11 and is guided so as to be vertically movable therein. A spring 16 is tightened between the pin 15 and the center pin 11.

The valve action surface component 14 is connected to a guide member 18 by a joint 17. The joint 17 is shown in the drawing as a cylindrical roller joint. Only a compressive force is always applied from the first component 14 to the second component 1.
8, the joint can be easily configured. It is also possible to simply provide the component 18 with a round groove in which the cylindrical roller-shaped projecting surface directly machined on the component 14 comes into contact. The second component or guide member 18 is supported by roller bearings 19 on a flat guide surface 20 of the housing cover 21 . Casing cover 2
1 is connected to the casing 1 by screws 32.

A passage 35 in the valve action surface 13 is connected to a passage 36 in the valve action surface constituting member 14.
The opening 22 of No. 6 opens in the side wall of the valve action surface forming member 14 . This side wall is perpendicular to the axis of the joint 17 and therefore parallel to the plane in which the axis of rotation of the cylinder drum 10, i.e. the central axis of the central pin 11, can pivot. A flat casing wall 38 is attached to this wall 37 of the valve face component 14.
facing each other, a passage opening is provided in this wall 38 of the housing 1, in which a sealing element 39 is always in contact with the surface 37 and at every position of the valve-acting surface component 14. It is arranged so as to face the opening 22 and other parts are covered by the valve action surface forming member 14. In order to achieve a reliable seal, this sealing element is pressed against the wall 37 by a spring 40. Furthermore, the pressure of the liquid additionally generates a compressive force. A similar arrangement is provided symmetrically on the opposite side of the valve face component 14.

Instead of the illustrated sealing member 39 and spring 40 assembled to the casing wall 38, a sealing member having a through hole may be arranged within the opening 22 of the side wall 37 of the valve action surface forming member 14. This sealing member is also provided with a pressure spring behind it.

In order to be able to adjust the guide element 18 along a planar guide surface 20, an adjusting cylinder 23 is arranged in the guide element 18, in which a movable adjusting piston 24 is connected to the casing by means of a threaded connection 26. 1 and has a vertical hole 25 through which regulating pressure fluid can be introduced into the regulating cylinder 23. Laterally offset from this, but parallel to this, another adjusting piston 27 is arranged in the guide element 18, which inserts into the corresponding adjusting cylinder of the guide element 18 and applies an adjusting pressure to the adjusting cylinder. It is equipped with corresponding holes for supplying liquid. Connections 28 are provided on both sides for connecting regulating pressure fluid conduits.
Since a large force acts on the guide member 18 toward the right in FIG. 1 due to the inclination of the guide surface 20 with respect to the axis of the cylinder drum, two adjusting pistons 24 and their associated adjusting cylinders 23 are provided symmetrically and Only one adjusting piston 2 between these
It is appropriate to provide 7.

In order to increase the swivel angle, pressure fluid is removed from the cylinder 23 via the bore 25 and at the same time fluid is introduced into the corresponding adjusting cylinder by the bore of the piston 27. Conversely, in order to reduce the swivel angle, pressure fluid is introduced into the regulating cylinder 23 via the bore 25 in the regulating piston 24 and fluid is removed from the associated regulating cylinder by means of the bore in the regulating piston 27.

When changing the turning angle, the center pin 11 has a spherical head 1
Rotate around the center point of 2. The cylinder drum 10 is guided on this center pin 11,
The axes of rotation of the cylinder drum 10 therefore pivot together. However, each part of the center pin 11 moves in an arc about the center point of the spherical head 12, while the cylinder drum 10 moves on a trajectory defined by the valve action surface component 14, and the cylinder drum 10 moves on a trajectory defined by the valve action surface component 14, The movement of the surface element 14 itself is defined by the movement of the guide element 18 along the planar surface 20. As a result of this, the cylinder drum 10 moves significantly over the central pin 11 and thus on the piston 8 towards the drive flange 5 as the swivel angle decreases. As a result of this movement of the cylinder drum 5 in the direction of contraction, only a small clearance volume is left in the cylinder 9 in front of the piston 8. This clearance volume is much smaller than the size of the clearance volume that would occur if the cylinder drum 10 were to move along an arc centered on the center point of the spherical head 12 as in the prior art. A snap spring 29 is installed in the cylinder drum 10, and a snap spring 3 is mounted on the pin 15.
0 is attached. This Snut Spring 29
A pressure spring 31, which is designed as a tension spring, is tightened between and 30. In order to be able to use the compression spring as a compression spring as usual,
The two support members of the spring are arranged in a different manner, with the support member (snap spring) mounted on the cylinder drum being close to the valve action surface and the support member (snap spring) connected to the pin 15 being close to the valve action surface. It must be placed far away from the

In the illustrated embodiment, the guide surface 20 is perpendicular to the axis of the drive shaft 2. If the cylinder drum 10 is not rotated and the drive flange 5 and guide surface 2
If the distance from 0 is set small, the minimum clearance volume can be obtained without rotating the cylinder drum 10. However, such a minimum clearance volume cannot be obtained when the cylinder drum 10 is rotated as shown in the figure. This is because the distance between the drive flange 5 and the cylinder drum 10 is relatively large in advance due to the inclination (angle 104) of the end surface 101 of the piston 8, and even if the cylinder drum 10 is in the maximum rotation state, it will not be possible to contract. This is because the edge 103 of the end surface 101 of the piston 8 (the right-hand piston in the figure) must be set large enough to prevent it from abutting against the inner end surface 102 of the cylinder 9. In short, guide surface 2
0 is perpendicular to the axis of the drive shaft 2, no minimum clearance volume is obtained with the cylinder drum 10 swiveled. This point can be improved as follows. That is, guide surface 2
0 is a slightly inclined surface (angle 105) with respect to the axis of the drive shaft 2, so that the cylinder drum 10 occupies a position closer to the drive flange 5 when it is not pivoted than when it is pivoted. That's what I do. In this way, the edge 103 of the end face 101 of the piston 8 will have the required minimum spacing in front of the inner end face 102 of the cylinder 9.

Note that instead of the rolling bearing (roller bearing) 19, any known bearing such as a sliding bearing or a hydraulic bearing can be used.

Another advantage of the configuration of the invention over known machines with cylindrical or spherical surfaces is that the overall length of the machine is reduced, especially when the adjusting cylinder is retracted into the guide member 18 as shown. This is what is happening.

Overall, the following advantages result compared to previously known machines with hollow cylindrical guide surfaces in the casing: (1) The overall machine is shorter. That is, in the known case, the component having the valve-acting surface pivots on a circular path about the pivot axis of the cylinder drum when adjusting the pivot angle of the cylinder drum. Therefore, even when the stroke volume is small, the distance between the pivot axis and the component is the same as when the stroke volume is large, and as a result, in the axial direction of the drive shaft, even when the swing angle is small, the distance between the drive flange component and the component is the same as when the stroke volume is large. The distance between them increases. In contrast, in the case of the present invention, this component with the valve-acting surface moves linearly in a plane approximately perpendicular to the axis of the drive flange, so that this component has a small pivot angle. Sometimes it occupies a position closer to the drive flange than when the swing angle is large. The machine can therefore be designed shorter.

(2) The volume of the gap is reduced, which in turn improves efficiency. That is, as the component having the valve action surface moves in a straight path, the cylinder drum moves from a large swing angle position to a small swing angle position, and the cylinder drum moves over the piston in a contracting direction. movement, resulting in a reduction in the gap volume.

(3) Manufacturing becomes easier. That is, in the case of the known example, it was necessary to precisely machine cylindrical surfaces with a large radius of curvature on the component member having the valve action surface and the casing, respectively, with the same radius of curvature, but in the case of the present invention, it was necessary to precisely machine the cylindrical surface with the same radius of curvature on the component having the valve action surface and the casing. The linear movement of the guide element as a second component simplifies the processing technique considerably.

(4) The adjusting cylinder for the guide member and thus the cylinder drum can be integrated in an advantageous manner without the need for a mechanism for converting the linear movement of this adjusting cylinder into a pivoting movement of the pivoting part. That is, conventionally, a movement mechanism has been required to convert the linear movement of this type of adjustment cylinder into the rotational movement of a component having a valve-acting surface. Moreover, this transformation of motion must be carried out with as little play as possible.
Due to pressure fluctuations, undesired relative movements occur between the component and the adjusting piston. In the case of the present invention, such a motion conversion mechanism is not required. This is because the guide element moving within the housing produces a linear motion, so that the adjusting piston can be connected directly to this guide element. In the illustrated embodiment, the guide element itself constitutes an adjusting cylinder.

If no special configuration is provided, the axis of the cylinder drum in the machine according to the invention is always centered at the point where the drive flange axis passes through the plane of arrangement of the spherical head of the piston rod in the drive flange 5. rotate. In this embodiment, this pivoting movement is enabled and forced by a central pin 11 with a spherical head 12. However, other embodiments are also conceivable. However, the cylinder drum does not always make an arc-shaped turning movement around one turning axis.
A movement in the cylinder drum axis direction is superimposed on this arcuate movement.

[Brief explanation of the drawing]

The accompanying drawings show an embodiment of the invention, in which FIG. 1 is a sectional view in a plane containing the drive shaft axis and the cylinder drum axis, and FIG. 2 shows the drive flange, drive shaft and corresponding casing parts. A sectional view taken in a direction perpendicular to the cutting plane of FIG. 1 and including the cylinder drum axis, shown removed; FIG. 3 shows the valve action surface component perpendicular to the cylinder drum axis. FIG. The correspondence relationship between the main parts shown and the symbols is as follows; 1...Casing, 2...Drive shaft, 5...Drive flange, 8...Piston, 9...Cylinder, 1
0... Cylinder drum, 13... Valve action surface, 14
... Valve action surface constituent member, 18 ... Guide member, 20
...Guidance surface, 22...Opening, 35 and 36...
aisle.

Claims (1)

[Scope of Claims] 1. The cylinder drum is supported by one component, and this component has a valve action surface,
Two approximately semicircular passages each open in the valve-acting surface, both passages passing through the interior of the component having the valve-acting surface, the second opening of which opens into the component. The cylinder drum rotates about an axis that intersects and is tiltable relative to the axis of the drive flange shaft, in each case facing an opening of a passage arranged in the casing. In a format that can be
Component 14 with a valve-acting surface in an axial piston machine with a variable displacement drive flange
has an axis perpendicular to a plane containing the axis of the cylinder drum 10 and the axis of the drive shaft 2.
Via two joints 17, it is tiltably supported on a second component 18 as a guide element, which second component 18 is supported on a flat surface 20 of the housing and rests on this surface 20. A driving flange type axial piston machine characterized by being capable of linear movement via a bearing member. 2. The driving flange type axial piston machine according to claim 1, wherein the axis of the joint 17 intersects with the rotational axis of the cylinder drum 10. 3. According to claim 1, both passages in the valve-acting surface-constituting member 14, each emanating from one passage of the valve-acting face-constituting member, open into a respective one of the side walls of the valve-acting face-constituting member. Drive flange type axial piston machine. 4. Each of the passages within the valve action surface component 14 is movable by the pressure within the passageway.
Axial piston machine with drive flange according to claim 3, which communicates with opposing openings in the wall of the casing 1 by means of a sealing member arranged therein and having a through hole. . 5. The drive flange type axial piston machine according to claim 1, wherein a linear guide surface 20 is formed by a flat surface within the casing cover 21, and the guide member 18 is in contact with this linear guide surface 20. 6. The drive flange type axial piston machine according to claim 5, wherein the guide surface 20 of the guide member 18 is substantially perpendicular to the axis of the drive shaft 2. 7. If a hydraulic device is provided for adjusting the pivoting position of the cylinder drum, the adjusting cylinder 23 is disposed within the guide member 18 and the adjusting pistons 24, 27' are supported by the casing 1. A driving flange type axial piston machine according to claim 1. 8. The driving flange type axial piston machine according to claim 7, wherein a vertical hole 25 is provided in the regulating piston 24 for supplying regulating pressure fluid to the regulating cylinder 23. 9. Axial piston machine with drive flange according to claim 1, in which the central pin is guided longitudinally displaceably in a component having a valving surface (13). 10. The drive flange type according to claim 1, in which a further pin 15 is telescopically guided in the center pin 11 and is mounted in the valve action surface component 14. Axial piston machine. 11. The driving flange type axial piston machine according to claim 10, wherein the pin 15 is connected to the joint 17 between the valve action surface forming member 14 and the guide member 18. 12 When a compression spring is provided between the cylinder drum and the valve action surface, the compression spring 31 is placed between the cylinder drum 10 and the valve action surface component 14, particularly between the cylinder drum 10 and the valve action surface component 14. The driving flange type axial piston machine according to claim 10, which is tightened between the coupled pin 15. 13 The guide surface 20 that guides the guide member 18 is arranged on the drive shaft axis so that the clearance volume between the piston end face and the cylinder end face in the cylinder drum has the smallest possible value at every pivot position on the cylinder drum axis. 6. A driven flange axial piston machine according to claim 5, which is slightly inclined from a plane perpendicular to the axis.