Axial piston machine with controlled cylinder pressure and control flap regulated by means of a regulator

Abstract

The present invention relates to an axial piston machine (10) having a cylinder (60) rotatable about a rotation axis (30), the cylinder having an end face (63) pointing in the direction of the rotation axis (30), wherein the end face (63) is capable of being pressed toward a control surface (54) by a piston-cylinder-unit (80) in the direction of the rotation axis (30), wherein the piston-cylinder-unit (80) is capable of being loaded with a control pressure for this purpose, wherein the control surface (54) is arranged to resist torsion. According to the invention, the control pressure (85) is provided by an adjustable control valve (90), wherein the control valve (90) is connected to a control device (92) such that it can be adjusted by the control device (92), wherein the control device (92) implements a regulator (100), the adjustment parameter (101) of which affects the adjustment of the control valve (90).

Description

Technical Field

[0001] This invention relates to an axial piston machine. Background Technology

[0002] An axial piston machine with a swashplate structure is known from DE 39 04 782 A1. A piston-cylinder unit is arranged between the drive shaft and the cylinder, the end face of which can be pressed against a control face by the piston-cylinder unit. The control pressure applied in the piston-cylinder unit is extracted from the control clearance, in which high pressure is applied. Summary of the Invention

[0003] The advantage of this axial piston press is that leakage between the end face and the control face is minimal under all operating conditions. This axial piston press can operate at particularly high speeds and at particularly high pressures.

[0004] According to the technical solution of the present invention, an axial piston machine having a cylinder rotatable about a rotational axis is proposed. The cylinder has an end face pointing in the direction along the rotational axis, wherein the end face can be pressed towards a control surface by a piston-cylinder unit in the direction of the rotational axis, wherein the piston-cylinder unit can be loaded with a control pressure for this purpose, and wherein the control surface is arranged to resist torsion. According to the invention, the control pressure is provided by an adjustable control valve, wherein the control valve is connected to a control device such that it can be adjusted by the control device, wherein the control device implements a regulator whose adjustment parameters affect the adjustment of the control valve, wherein the control pressure is connected to a first pressure sensor, wherein the first pressure sensor is connected to the control device, wherein the actual parameter of the regulator is the measurement value of the first pressure sensor, and wherein the rated parameter of the regulator can be selected at least according to the high pressure of the axial piston machine. The axial piston machine is preferably implemented with a swashplate structure, wherein the cylinder-piston unit is supported on a drive shaft. The axial piston machine can also be implemented with a swashplate structure. The control valve is preferably electrically adjustable. The control device preferably includes a digital computer, wherein the regulator is implemented digitally. The regulator is preferably a continuous, linear regulator, and is preferably calculated in a time-discrete manner. The regulator is preferably a PI regulator.

[0005] The present invention also relates to other advantageous extensions and improvements.

[0006] As described above, the control pressure is connected to a first pressure sensor, which is connected to the control device. The actual parameter of the regulator mentioned is the measurement value of the first pressure sensor, and the rated parameter of the regulator can be selected at least according to the high pressure of the axial piston machine. It is also conceivable to use a sensor to determine the actual parameter, which directly measures the thickness of the hydrostatic lubricating film between the end face and the control face. Ultimately, this thickness should have a defined value, thereby achieving essentially complete hydraulic unloading between the end face and the control face with minimal leakage. However, such a fluid film-thickness sensor is extremely expensive. Similar results can be obtained using the proposed, much less expensive first pressure sensor, if the assigned rating is selected as suggested.

[0007] "Complete hydraulic unloading" refers to a state in which there is no mechanical contact between the end face and the control face, where the pressure is transmitted hydrostatically through a pressurized fluid used in the axial piston mechanism. The pressurized fluid is preferably a liquid and at most preferably hydraulic oil. The axial piston mechanism preferably has first and second working joints, wherein rotation of the cylinder is accompanied by fluid flow between the first and second working joints. The axial piston mechanism is capable of four-quadrant operation, meaning it can operate not only in two opposite directions of cylinder rotation but also in two opposite flow directions along each direction of rotation, regardless of the pressures applied to the first and second working joints. The high pressure is the higher of the pressure on the first working joint and the pressure on the second working joint. The high pressure is preferably connected to a second pressure sensor. The second pressure sensor is preferably connected to the control device.

[0008] It can be specified that at least one first combined characteristic curve is stored in the control device, the first combined characteristic curve serving as an input parameter having at least the high voltage, and the first combined characteristic curve serving as an output parameter having the rated parameter of the regulator. The first and / or the second combined characteristic curve, to be mentioned below, can be implemented in the form of a numerical table. The first and / or the second combined characteristic curve can also be implemented using mathematical interpolation formulas. A hybrid form of these two implementations is also possible. It is possible that the first and the second combined characteristic curve, to be explained below, are thus determined experimentally using the fluid film-thickness-sensor mentioned above, thereby producing the desired ratio. It is also possible that the first and / or the second combined characteristic curve are determined through computer simulation.

[0009] It can be specified that the first combined characteristic curve, as an additional input parameter, includes the cylinder rotational speed and / or the rotation angle of the axial piston mechanism and / or the viscosity of the pressurized fluid. The axial piston mechanism preferably has an adjustable displacement volume. For a swashplate mechanism, the rotation angle describes the necessary deflection of the swashplate. For a swashplate mechanism, the rotation angle describes the angle between the rotation axis of the drive shaft and the rotation axis of the cylinder. The viscosity of the pressurized fluid is preferably determined using a temperature sensor, wherein its viscosity is determined from the corresponding measured values ​​and the temperature-viscosity-characteristic curve of the pressurized fluid.

[0010] A fluid source can be provided to supply pressurized fluid to the control valve. The fluid source is preferably formed by a first and / or a second working connector. The first and second working connectors can be connected to a directional control valve on the input side, and the control valve can be connected to the directional control valve on the output side. The fluid source can also be formed by a separate control oil pump.

[0011] It can be specified that the control valve includes a single, continuously adjustable control baffle, the opening cross-section of which can be adjusted by the control device. Preferably, there is a time-varying correlation between the corresponding adjustment signal on the control valve and the opening cross-section of the control baffle. In particular, the correlation mentioned is not defined by another lower-level control loop. For example, the adjustment current on the control valve is approximately proportional to the opening cross-section of the control baffle. The control valve is preferably a 2 / 2 proportional-directional valve, which is at most preferably configured as a directly controlled structure. A 3 / 2 proportional-directional valve can also be considered, which is additionally connected to a fluid absorption source, such as a substantially pressureless internal space of the housing or a tank. It is also possible to use a pressure-reducing valve as the control valve to adjust the control pressure hydraulically. However, with the simple control valve previously proposed, an improvement to the adjustment method, which is explained below, can be achieved, significantly improving the overall system stability without increasing hardware costs.

[0012] It can be specified that the adjustment of the control valve is determined by the adjustment parameters of the regulator and the pre-control parameters, wherein the pre-control parameters depend at least on the high pressure of the axial piston machine. This minimizes the duration until the adjusted state is reached. The stability of the adjustment is further improved. Preferably, the adjustment of the control valve is determined by the sum of the adjustment parameters of the regulator and the pre-control parameters.

[0013] It can be specified that the control device stores at least one second characteristic curve different from the first combined characteristic curve, wherein the second combined characteristic curve, as an input parameter, has at least the high pressure of the axial piston machine, and wherein the second combined characteristic curve, as an output parameter, has the pre-control parameter. The first and second combined characteristic curves can be summarized into a three-dimensional combined characteristic curve, that is, summarized as a combined characteristic curve with multiple output parameters. Conversely, the first and / or second combined characteristic curve preferably has only one unique output parameter.

[0014] It can be specified that the second combined characteristic curve, as an additional input parameter, includes the cylinder rotational speed and / or the rotational angle of the axial piston and / or the viscosity of the pressurized fluid. This allows the pre-controlled parameters to be flexibly adapted to different operating conditions of the axial piston.

[0015] It goes without saying that the features mentioned above and explained below can be used not only in the combinations described, but also in other combinations or individually, without departing from the scope of the invention. Attached Figure Description

[0016] The invention will now be explained in detail with reference to the accompanying drawings. Wherein:

[0017] Figure 1 A longitudinal section of an axial piston machine according to the invention is shown;

[0018] Figure 2 It shows according to Figure 1 Hydraulic circuit diagram of an axial piston machine;

[0019] Figure 3 It shows Figure 1 The portion selected within the piston-cylinder-unit region;

[0020] Figure 4 The longitudinal section of the cylinder is shown;

[0021] Figure 5 It shows according to Figure 4 Side view of the cylinder;

[0022] Figure 6 A perspective view of the control panel is shown; and

[0023] Figure 7 It shows according to Figure 1 Circuit diagram for adjusting the axial piston machine. Detailed Implementation

[0024] Figure 1A longitudinal section of an axial piston machine 10 according to the invention is shown. The axial piston machine 10 includes a housing 40, which is composed of first and second housing members 41 and 42. The first housing member 41 is implemented in a canister shape, with its open side covered by a plate-shaped second housing member 42, thereby creating a closed internal space. In the housing 40, a drive shaft 33 is supported by first and second rotary bearings 31 and 32 in a manner rotatable about a rotation axis 30. The first and second rotary bearings 31 and 32 are configured as tapered roller bearings. The drive shaft 33 extends from the housing 40 via a journal 34, which is provided with a splined shaft tooth.

[0025] Inside the housing 40, the drive shaft 33 is surrounded by a cylinder 60, which is connected by a splined shaft tooth (in... Figure 4 (Ref. 66) is torsionally connected to the drive shaft 33 about the axis of rotation 30. The cylinder 60 has an end face 63 pointing along the axis of rotation 30, with which it rests against the control surface 54. The end face 63 is flat and arranged perpendicular to the axis of rotation 30. However, an end face 63 that is rotationally symmetrical about the axis of rotation 30, for example, is concavely curved, can also be used. The latter is commonly used, for example, for axial piston machines with a slanted shaft structure. A plurality of linearly movable working pistons 13 are received in the cylinder 60, preferably evenly distributed around the axis of rotation 30. The axis of motion of the working pistons 13 is arranged slightly inclined relative to the axis of rotation 30.

[0026] The control surface 54 is arranged on a separate control plate 50, which can also be directly arranged on the housing 40. The control plate 50 is torsionalally connected to the housing 40 about the axis of rotation 30, and is supported on the housing 40 along the direction of the axis of rotation 30. Therefore, during operation of the axial piston mechanism 10, relative rotation occurs between the end face 63 and the control surface 54, where a hydrostatic lubricating film is formed. An advantage of this invention is that leakage caused by this lubricating film is minimal under all operating conditions, with minimal wear also observed. The axial piston mechanism 10 is particularly capable of operating at high pressures and / or high speeds.

[0027] This axial piston press 10 is constructed with a swashplate structure, and the invention can also be applied to axial piston presses with a swashplate structure. The swashplate 15 is capable of rotation about a rotation axis arranged perpendicular to the rotation axis 30. Here, the rotation axis intersects the rotation axis 30, and the rotation axis can also be arranged at a certain distance relative to the rotation axis 30. The working pistons 13 are supported on the flat surface of the swashplate 15 by slides 14, wherein the corresponding contact surfaces are preferably hydraulically unloaded. The rotation angle of the swashplate can be adjusted by means of first and second adjusting cylinders 16 and 17, each configured as a single-function cylinder. This axial piston press 10 is capable of zero-crossing adjustment, meaning that the flow direction can be reversed simply by deflecting the swashplate 15, without changing the rotation direction of the cylinder. However, the present invention can also be applied to axial piston machines that can only be adjusted in one direction starting from zero displacement volume, or to axial piston machines whose displacement volume is constant.

[0028] It should also be noted that the piston-cylinder unit 80, the cylinder 60, can be hydraulically pressed against the control surface 54 by means of the piston-cylinder unit, wherein further details are provided in the section on... Figure 3 Explanation.

[0029] Figure 2 It shows according to Figure 1 The hydraulic wiring diagram of the axial piston machine 10. The axial piston machine 10 has first and second working joints 11 and 12, which are arranged in the second housing member (in...). Figure 1 (See reference numeral 42 in the attached figure). The axial piston machine 10 here has four-quadrant capability, that is, it can operate with two opposite directions of rotation of the drive shaft, wherein two opposite flow directions are possible in both cases. The pressure on the first and second working joints 11, 12 can be largely arbitrary. Therefore, the axial piston machine 10 can operate alternately as a pump and as a motor. The drive shaft of the axial piston machine 10 is in a rotary drive connection with the motor 12, which can be implemented as an electric motor or constructed as a combustion motor. The rotation of the drive shaft is accompanied by fluid flow between the first and second working joints 11, 12 if the adjusted displacement volume is not equal to zero.

[0030] The adjusted rotation angle and, indirectly, the displacement volume can be measured using rotation angle sensor 113. The temperature of the pressurized fluid and, indirectly, its viscosity can be measured using temperature sensor 115, which can be connected to the first and second working joints 11, 12. The rotational speed of the drive shaft or cylinder can be measured using speed sensor 114.

[0031] The first and second working connectors 11 and 12 are connected to the directional control valve 22 on the input side. The output side of the directional control valve is thus loaded with the higher of the pressure on the first working connector 11 and the pressure on the second working connector 12. This pressure is referred to as high pressure 20 within the scope of this application. This high pressure is used herein as a fluid source 21 for supplying pressurized fluid to the control valve 90. It should be noted that a separate control oil pump can also be used as the fluid source. The high pressure 20 is measured herein using a second pressure sensor 112.

[0032] The high pressure 20 is conducted through the control valve 90 to two transition gaps 55 in the control plate 50, which are connected in parallel to the control valve 90. The control valve 90 includes a continuously adjustable control baffle 91, the opening cross-section of which is adjustable from zero to a predetermined maximum value. The adjustment is preferably made electrically, at most by means of an electromagnet 94, the adjusting force of which acts directly on the valve core or valve cone of the control valve 90. The control valve 90 is pre-tightened to a locked position by means of a spring 93. This control valve is configured as a 2 / 2 directional proportional valve. The pressure applied downstream of the control baffle 91 is called the control pressure 85. The control pressure 85 is measured by means of a first pressure sensor 111. All of the above are... Figure 2 Sensors 111, 112, 113, 114, and 115, shown in the diagram, are connected to a control device 92, where the electromagnet 94 of the control valve 90 is also connected, allowing the control valve 90 to be adjusted by the control device 92. The control device 92 implements the following... (refer to...) Figure 7 The described adjustment. The control device preferably includes a programmable digital computer.

[0033] Figure 3 It shows Figure 1 The portion cut off in the region of the piston-cylinder-unit 80. The piston-cylinder-unit 80 includes first and second annular pistons 81 and 82, which are respectively received between the drive shaft 33 and the cylinder 60. Correspondingly, preferably cylindrical contact gaps about the axis of rotation 30 are respectively sealed substantially fluid-tightly with sealing rings 86, especially O-rings. The first annular piston 81 faces away from the control surface along the direction of the axis of rotation 30 (in Figure 1(See reference numeral 54 in the attached figure) is form-fitted on a shoulder on the drive shaft 33. The second annular piston 82 is oriented along the rotation axis 30 toward the control surface (in... Figure 1 (See reference numeral 54 in the attached diagram) is supported on the cylinder 60 by a safety ring 84. The cylinder 60, drive shaft 33, and first and second annular pistons 81, 82 together define a fluid chamber 84, which is substantially fluid-tightly closed except for the fluid passage 65. The cylinder 60 is capable of minimal movement relative to the drive shaft 33 along the axis of rotation 30, such that the control pressure 85 present in the fluid chamber 84 pushes the cylinder 60 toward the control surface (in... Figure 1 (See attached figure 54) Extrusion. The corresponding reaction force is supported by the drive shaft 33 on the first rotary bearing (in... Figure 1 As shown in the attached figure (reference numeral 31), the mounting positions of the corresponding tapered roller bearings were selected accordingly, such that the two tapered roller bearings form an O-type arrangement.

[0034] Furthermore, the protrusions 83 on the first and second annular pistons 81, 82 should be noted. These protrusions are arranged such that the first and second annular pistons 81, 82 do not cover the orifice 68 of the fluid passage. Additionally, the corresponding surface—where the first and second annular pistons 81, 82 can contact—is implemented relatively small relative to the overall end face of the first or second annular pistons 81, 82. Thus, in each position of the annular pistons 81, 82, it is ensured that the control pressure 85 causes a sufficiently large action of the cylinder 60 on the control surface (in...). Figure 1 Sufficient clamping force on the attached figure (54).

[0035] Figure 4 A longitudinal section of the cylinder 60 is shown. Cylinder bores 64 can be seen, all of which are implemented identically. Each cylinder bore 64 has a cylindrical section 67 into which the working piston (in...) is distributed. Figure 1 (See reference numeral 13 in the attached figure) is received in the cylindrical section in a linearly movable and substantially fluid-sealed manner. The cylindrical section can be formed by a single bushing made of a sliding bearing material such as bronze. The cylinder bore 64 opens to the end face 63 via a first orifice 61. The cross-sectional area of ​​the first orifice 61 can be the same as or slightly smaller than the cross-sectional area of ​​the cylindrical section 67. In the latter case, the cylinder 60 is pressed against the control face (in the...) solely by the hydraulic pressure in the cylinder bore 64. Figure 1 The result is shown in the attached figure (reference numeral 54). Within the scope of the invention, this force is related to the ability to use the piston-cylinder unit (in... Figure 3The force obtained (reference numeral 80) is relatively small, allowing for meaningful adjustment of the corresponding clamping force. The invention allows for a particularly large first orifice 61, ensuring that the axial piston mechanism does not form cavitation in the intake region even at high rotational speeds of the cylinder 60.

[0036] Fluid passages 65 are arranged between two adjacent cylinder bores 64, extending obliquely relative to the axis of rotation 30 such that they open to the end face 63 via a second orifice 62, and at their opposite ends to the fluid chamber via a third orifice 68. Figure 3 (See reference numeral 84 in the attached figure). All fluid channels 65 are constructed identically to each other. The fluid channels are implemented in a straight line, wherein they are implemented here as cylindrical graded orifices. The section forming the second orifice 62 here has a smaller diameter than the other section. Thus, the allocated transition gap (in Figure 6 The surface of the figure (reference numeral 55) is minimized so that the hydraulic pressure acting there is less than the force of the piston-cylinder unit.

[0037] The cylinder barrel 60 is constructed as a single piece. Particularly in the cylindrical section 67 and the end face 63, the cylinder barrel undergoes surface hardening treatment, such as carburizing and nitriding. The cylinder barrel 60 is made of, for example, steel or cast iron.

[0038] Figure 5 It shows according to Figure 4 A side view of the cylinder 60. It can be seen that the first orifice 61 has a shape other than circular. Its width in the radial direction is particularly smaller than its length in the circumferential direction. The first orifice 61 is arranged as close as possible to the spline shaft tooth 66 so that a particularly small centrifugal force acts on the pressurized fluid there. This measure allows for an increase in the maximum permissible rotational speed of the cylinder 60. The first orifice 61 defines a reference circle 70, the center of which is the axis of rotation 30. The radially outermost point of each first orifice 61 lies on this reference circle 70. All second orifices 62 are arranged radially outside the reference circle 70. Thus, at any position in the cylinder 60, the cylinder bore 64 is in contact with the control pressure (in... Figure 2 There is no direct fluid connection between the components (see attached figure 85). In other words, the fluid connection is always via an adjustable control baffle (in...). Figure 2 (See attached figure 91) for details.

[0039] Here, a total of nine cylinder bores 64 are provided, which are evenly distributed around the rotation axis 30. Between each of the cylinder bores 64, a fluid channel with a corresponding second orifice 62 is arranged. The spacing between all the second orifices relative to the rotation axis 30 (in...) Figure 4 The same implementation is applied to all of the figures (reference numeral 71). In principle, it is possible to consider providing fluid passages only between a portion of the cylinder bores 64. The subsequent transition clearance (in...) Figure 6 The figure in Figure 55) must extend over a larger area in the surrounding region, thereby generating greater hydraulic pressure there, which is undesirable.

[0040] Figure 6 A perspective view of the control panel 50, more precisely from the control surface 54, is shown. The control panel 50 is substantially implemented as a flat plate with a constant thickness. Figure 6 The back side, invisible from the outside, is completely flat. In contrast, the control surface 54 has an inner annular gap 57, an annular groove 56, and an outer annular gap 58. The inner annular gap 57 and the annular groove 56 define a surface on which the control surface 54 rests against the end face of the cylinder in the regions of the first and second control gaps 51, 52. This surface defines the leakage that occurs there. This surface is designed to form a hydrostatic lubricating film so thick under all operating conditions that the end face is substantially completely separated from the control surface 54. However, the lubricating film should not be thicker.

[0041] The first and second control gaps 51 and 52 are respectively constructed as circularly curved elongated holes, with the respective centers defined by the rotation axis 30. The control gaps are located relative to the first orifice of the cylinder (in...). Figure 6 The reference numerals 61 in the attached diagram are aligned. They are provided with notches 53 at both ends along the circumferential direction, which minimize the pressure peaks during the operation of the axial piston press. The first and second control gaps 51, 52 pass through the control plate 50 along the direction of the rotation axis 30. The control gaps are constructed in a mirror-symmetric structure because this axial piston press has a four-quadrant capability.

[0042] Two transition gaps 55 are arranged between the annular groove 56 and the outer annular gap 58. These transition gaps pass through the control plate 50 along the direction of the rotation axis 30. Each transition gap is constructed as a circularly curved elongated hole, with the corresponding center defined by the rotation axis 30. The radial width of each transition gap is equal to the corresponding width of the second opening (in...). Figure 4(See reference numeral 72 in the attached figure), wherein the transition gap is arranged aligned with these second orifices. The length of the transition gap along the circumferential direction is thus selected such that at least one second orifice is above the transition gap 55 in each rotational position of the cylinder. The length of the transition gap is greater than the length of the second orifice in the... Figure 5 The visible spacing is slightly larger than half of the total spacing. The two transition gaps 55 are arranged in a mirror image of each other. It goes without saying that any number of transition gaps 55 can be used, provided that their length along the perimeter is designed accordingly.

[0043] The annular groove 56 has a second through-hole 132 at its bottom, which passes through the control plate 50 along the direction of the rotation axis 30. There, leakage accumulated in the annular groove 56 is directed toward the interior space of the housing for further guidance into the reservoir via a leakage connector on the housing. The first through-hole 131 in the center of the control plate 50 is driven by a shaft (in... Figure 1 (See attached figure 33) Crossing.

[0044] Figure 7 It shows according to Figure 1 A circuit diagram for the regulation of an axial piston machine. The corresponding regulator 100 is preferably a continuous linear regulator, wherein the regulator is implemented, for example, as a PI regulator. The regulation deviation 105 is formed by the difference between the rated parameter 103 and the actual parameter 102. The actual parameter is the control pressure measured by the first pressure sensor 111. The rated parameter 102 is determined by means of a first combined characteristic curve 121. The input parameter of the first combined characteristic curve is a high pressure measured by the second pressure sensor 112, wherein the measurements of the speed sensor 114 and / or the rotation angle sensor 113 and / or the temperature sensor 115 can be used as additional input parameters. The first combined characteristic curve 121 is designed such that the regulation produces a substantially constant thickness of the hydrostatic lubricating film between the end face of the cylinder and the control surface.

[0045] The regulating parameter 101 of the regulator acts on the regulating valve 90. This regulating valve 90 can include a single adjustable control baffle 91 because unavoidable leakage will cause the control pressure (at...) Figure 2 The continuous reduction of (reference numeral 85) in the figure, if this effect is not overcome by the corresponding opening of the control baffle 91.

[0046] It has been shown that exceptionally stable system performance can be achieved through this particularly simple adjustment.

[0047] The regulator 100 can be supplemented by pre-control. A corresponding pre-control parameter 104 is preferably added to the regulation parameter 101 of the regulator 100. The regulation parameter 104 can be determined using a second combined characteristic curve 122. The input parameter of the second combined characteristic curve 122 can be the measured value of the second pressure sensor 112 and / or speed sensor 114 and / or rotation angle sensor 113 and / or temperature sensor 115. The second combined characteristic curve (Kennfeld) 112 can be determined, for example, by running the system without pre-control using constant measured values ​​from the aforementioned sensors until the constant regulation parameter 101 reaches an average value. This regulation parameter is then used as the pre-control parameter. This measure shortens the time required to reach the adjusted state.

[0048] List of reference numerals in the attached diagram:

[0049] n cylinder rotation speed

[0050] T is the temperature of the pressure fluid.

[0051] α rotation angle

[0052] 10 Axial Piston Press

[0053] 11 First working joint

[0054] 12 Second working joint

[0055] 13 Working piston

[0056] 14 Slide

[0057] 15-inch rotating cradle

[0058] 16 First regulating cylinder

[0059] 17 Second Adjusting Cylinder

[0060] 20 High Voltage

[0061] 21 Fluid Source

[0062] 22 Reversing valve

[0063] 23 motors

[0064] 30 Rotation axis

[0065] 31 First Rotary Bearing

[0066] 32 Second Rotary Bearing

[0067] 33 drive shaft

[0068] 34 journals

[0069] 40 Housing

[0070] 41 First housing component

[0071] 42 Second housing component

[0072] 50 Control Board

[0073] 51 First control gap

[0074] 52 Second control gap

[0075] 53 Gap

[0076] 54 Control Surface

[0077] 55. Transfer gap

[0078] 56 Annular groove

[0079] 57 The annular gap inside

[0080] 58. The outer annular gap

[0081] 60 cylinder barrel

[0082] 61 First Orifice

[0083] 62 Second Orifice

[0084] 63 End face

[0085] 64 cylinder bore

[0086] 65 Fluid Channel

[0087] 66 Splined Shaft Gear

[0088] 67. Cylindrical section of cylinder bore

[0089] 68 Third Orifice

[0090] 70 reference circle

[0091] 71 Radial distance of the second orifice relative to the axis of rotation

[0092] 72. Diameter of the second orifice measured radially.

[0093] 80 Piston-Cylinder-Unit

[0094] 81 First Ring Piston

[0095] 82 Second Ring Piston

[0096] 83 Highlighted parts

[0097] 84 Fluid Chamber

[0098] 85 Controlling Pressure

[0099] 86 Sealing ring

[0100] 87. Safety Ring

[0101] 90 Control valve

[0102] 91 Control panel

[0103] 92 Control device

[0104] 93 Springs

[0105] 94 Electromagnets

[0106] 100 regulator

[0107] 101 Adjusting parameters

[0108] 102 Actual Parameters

[0109] 103 Rated Parameters

[0110] 104 Pre-control parameters

[0111] 105 Adjustment Deviation

[0112] 111 First pressure sensor

[0113] 112 Second pressure sensor

[0114] 113 Rotation Angle Sensor

[0115] 114 Speed ​​Sensor

[0116] 115 Temperature Sensor

[0117] 121 First combination characteristic curve

[0118] 122 Second combination characteristic curve

[0119] 131 First perforation

[0120] 132 Second perforation.

Claims

1. Axial piston machine (10) with a cylinder barrel (60) rotatable about an axis of rotation (30), the cylinder barrel having an end face (63) directed in the direction of the axis of rotation (30), wherein the end face (63) is able to be pressed in the direction of the axis of rotation (30) by a piston-cylinder unit (80) against a control face (54), wherein the piston-cylinder unit (80) is able to be loaded for this purpose with a control pressure (85), wherein the control face (54) is arranged in a torsionally rigid manner, characterized in that the control pressure (85) being provided by an adjustable control valve (90), wherein the control valve (90) is connected to a control device (92) in such a way that it is adjustable by the control device (92), wherein the control device (92) implements a regulator (100) whose regulating variable (101) influences the adjustment of the control valve (90), wherein the control pressure (85) is connected to a first pressure sensor (111), wherein the first pressure sensor (111) is connected to the control device (92), wherein the actual variable (102) of the mentioned regulator (100) is the measured value of the first pressure sensor (111), wherein the setpoint variable (103) of the regulator (100) is able to be selected at least as a function of a high pressure (20) of the axial piston machine (10).

2. Axial piston machine according to Claim 1, wherein at least one first combined characteristic curve (121) is stored in the control device (92), the first combined characteristic curve having at least the high pressure (20) as an input variable, wherein the first combined characteristic curve has the setpoint variable (103) of the regulator (100) as an output variable.

3. Axial piston machine according to Claim 2, wherein a fluid source (21) being provided, by means of which pressure fluid is supplied to the control valve (90), wherein the first combined characteristic curve (121) has as further input variables the rotational speed (n) of the cylinder barrel (60) and / or the swivel angle (a) of the axial piston machine (10) and / or the viscosity of the pressure fluid.

4. Axial piston machine according to any one of Claims 1 to 3, wherein the control valve (90) comprises a unique continuously adjustable control flap (91), wherein the opening cross section of the control flap (91) is adjustable by means of the control device (92).

5. Axial piston machine according to any one of Claims 1 to 3, wherein the adjustment of the control valve (90) is specified from the regulating variable (101) of the regulator (100) and a pre-control variable (104), wherein the pre-control variable (104) depends at least on the high pressure (20) of the axial piston machine (10).

6. Axial piston machine according to Claim 2, wherein at least one second combined characteristic curve (122) different from the first combined characteristic curve (121) is stored in the control device (92), wherein the second combined characteristic curve (122) has at least the high pressure (20) of the axial piston machine (10) as an input variable, wherein the second combined characteristic curve has as an output variable a pre-control variable (104) which depends at least on the high pressure (20) of the axial piston machine (10).

7. Axial piston machine according to claim 6, wherein a fluid source (21) is provided, by which the control valve (90) is supplied with pressure fluid, wherein the second combined characteristic curve (122) has as further input variables the rotational speed (n) of the cylinder barrel (60) and / or the swivel angle (a) of the axial piston machine (10) and / or the viscosity of the pressure fluid.

8. Axial piston machine according to claim 7, wherein the control device (92) is designed to determine the pre-control variable (104) by means of the second combined characteristic curve (122) and to output the pre-control variable (104) to the control valve (90).

9. Axial piston machine according to claim 8, wherein the control device (92) is designed to determine the pre-control variable (104) by means of the second combined characteristic curve (122) and to output the pre-control variable (104) to the control valve (90).

10. Axial piston machine according to claim 9, wherein the control device (92) is designed to determine the pre-control variable (104) by means of the second combined characteristic curve (122) and to output the pre-control variable (104) to the control valve (90).

11. Axial piston machine according to claim 10, wherein the control device (92) is designed to determine the pre-control variable (104) by means of the second combined characteristic curve (122) and to output the pre-control variable (104) to the control valve (90).

12. Axial piston machine according to claim 11, wherein the control device (92) is designed to determine the pre-control variable (104) by means of the second

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