JP2003507626A - Axial piston drive with continuously adjustable piston stroke - Google Patents

Abstract

The present invention is based on an axial piston drive having a continuously adjustable piston stroke, wherein a first tilt angle with respect to a drive shaft (10, 12, 170) and a longitudinal direction (20). A swash plate (16, 18, 174) provided on the bearing seat (14) located at (22), wherein the swash plate (16, 18, 174) is provided in the crank chamber. ) With a bearing bore (30) inclined at a second inclination angle (28) with respect to a vertical line (26), said swash plates (16, 18, 174) being adapted to control a piston (Stroke). 32, 34), and can be rotated in a certain angular range, and furthermore, the cylinders (36, 38, 40, Movably provided in 2), those comprising at least one piston (44, 46, 48, 50) connected to be driven to the swash plate (16,18,174). In the rotation operation from the maximum effective inclination angle (52) to the minimum effective inclination angle (54), an axial stroke operation of the swash plate (16, 18, 174) in a direction toward the piston (44, 46, 48, 50). (56) is overlapped and the axial movement of the swash plate in a direction away from the pistons (44, 46, 48, 50) during the rotation operation from the minimum effective inclination angle (54) to the maximum effective inclination angle (52). It is proposed to overlap operation (116).

Description

Detailed Description of the Invention

Description of the Prior Art The present invention relates to an axial piston drive with continuously adjustable piston stroke according to the characterizing clause of claim 1.

The use of axial piston drives with continuously adjustable piston strokes is particularly known for vehicular air conditioning systems, which serve as refrigerant condensers.

The main components of a vehicle air conditioner are a refrigerant condenser, a first heat exchanger, a so-called evaporator, a second heat exchanger, a so-called liquefier or in the case of a supercritical process a gas cooler, an expansion pipe and A tubular conduit that connects the components to each other. The role of the refrigerant condenser is to draw the refrigerant from the evaporator where it evaporates by absorbing heat at low pressure levels and to condense it at higher pressure levels. Then discharge the refrigerant to the second heat exchanger at higher pressure and temperature levels,
In the expansion tube, the refrigerant is returned to a pressure level corresponding to the evaporator pressure. This results in a closed circulation process.

The output of the refrigerant condenser is regulated continuously via the speed of the drive motor, and in the most energetic and most advantageous manner, in the case of axial pistons, via the piston stroke. Known axial piston drives or axial piston condensers for vehicle air conditioners comprise a drive shaft that operates via a pulley. In the crank chamber, the swash plate is fixed to the drive shaft so as not to rotate, and is supported so as to be inclined via a joint. To absorb the tensile and compressive loads, each such piston is connected to the swash plate via two hinge yokes, one on the bearing surface of the swash plate facing the piston and the other on the remote surface. It In their plane of contact with the bearing surface of the swash plate, the hinge yoke moves at full circumferential velocity with concomitant radial movement, and consequently on an elliptical orbit. Said hinge yokes are seated on their bearings of spherically shaped pistons on their circular surfaces, within a relatively small relative movement during operation.

Furthermore, the connection between the swash plate and the piston can be formed not only by the hinge yoke described above, but additionally by means of a wobble plate. The wobble plate is fixed against torsion with respect to the drive shaft by either the housing or the piston rod. The bearing between the swash plate and the wobble plate absorbs all relative movement. The wobble plate only makes a rocking motion as a result of the rotation of the swash plate.

The piston stroke and thus the output of the axial piston drive is adjusted by changing the tilt angle of the swash plate. The large tilt angle results in a long piston stroke and high power, and
A small tilt angle results in a short piston stroke and low power. Generally, the tilt angle of the swash plate is defined by two stops to a minimum and maximum value. Usually one or two guide pins are needed to guide the tilting movement in a defined manner and prevent jamming from occurring. The tilt limiter, such as a stop, is integrally formed with the guide pin.

If adjustment of the tilt angle from the maximum value to a smaller value shifts the top dead center of the piston in the cylinder in the direction of the swash plate, the already compressed gas cannot be exhausted completely. . The compression energy introduced into the gas cannot be used in the cooling process. As a result, a "loss space" is created between the piston and the valve plate of the cylinder, causing energy loss. In order to prevent the occurrence of this "loss space" and protect the top dead center of the piston, the swash plate is provided so that it can be displaced axially additionally with respect to the compression stress compression spring. The movement of the swash plate in the axial direction is
Usually limited by stop devices.

(Advantages of the Invention) An axial piston drive device according to the present invention includes a drive shaft and a radial bearing seat for a swash plate that is inclined at a first inclination angle with respect to the longitudinal direction of the shaft. . The bearing seat is mounted on a swash plate in the crank chamber and has a bearing bore inclined at a second angle with respect to a vertical line of the swash plate. The driving movement of the swash plate is caused by the connection to at least one piston moving in the cylinder. The swash plate is rotated on the bearing seat over a range of angles by the controller to allow adjustment of the tilt angle and thus piston stroke and power output.

The rotational movement from the maximum effective inclination angle to the minimum effective inclination angle should be superposed with the axial stroke movement of the swash plate in the direction towards the piston, the movement from the minimum effective inclination angle to the maximum effective inclination angle. It is proposed that axial stroke motions in the direction away from the piston should be superposed. The tilting moment acting on the swash plate is advantageously supported by the large bearing surface of the drive shaft. It is possible to prevent jamming and prolong the life of the axial piston drive device. Further, the axial stroke motion can prevent or minimize the loss of space created by the tilt motion. The top dead center of the piston in the cylinder can be maintained, losses are avoided and in particular the axial piston drive can be advantageously used as a condenser in an air conditioning system. This capacitor is designed as a pure swash plate capacitor or as a wobble plate capacitor.
Furthermore, the solution according to the present invention can be applied to a gear mechanism, a hydraulic pump, and the like.

The axial stroke operation is performed by, for example, a piston that moves in the axial direction,
It can be obtained by various methods which seem suitable to a person having ordinary skill in the art. However, it is particularly advantageous to connect the swashplate to the drive shaft by means of a screw thread, which produces an additional axial stroke movement from the rotational movement of the swashplate. With a little effort,
By selecting the appropriate screw pitch, the desired relationship between rotational movement and axial stroke movement can be created. This screw pitch is
Between a rotation angle of 180 °, the swash plate is advantageously configured to be axially shifted by half the maximum piston stroke. The top dead center of the piston stays at the same position along the cylinder track, preventing loss space and energy loss from occurring.

Further, the swash plate can be prevented from sensitively reacting to vibrations and impacts in both the axial direction and the radial direction as well as fluctuations in torque by suppressing the threads. This thread is preferably formed on a radial surface, but it can also be formed on an axial surface, for example in the shape of a ring wedge,
It may be formed into a shape such as a ring wedge counterpart. The number of threads may be one or many. For screws with multiple threads, swash plates with both minimum and maximum tilt angles, despite steep pitches, can be threaded onto the drive shaft at one or more places around the circumference. It can be advantageously ensured that it is firmly fixed. It is also possible to form the thread on a special component mounted on the drive shaft, for example an elliptic cylinder. In one embodiment, it is proposed that the thread is formed integrally with the drive shaft in order to save the number of additional components and the labor and cost of assembly. Said swash plate is advantageously rotatable in order to allow a particularly simple assembly and to allow the center of gravity of the shifted part to be displaced along a desired axis, in particular the shaft axis, during the shifting process. And is mounted on a sleeve that is displaceable in the axial direction.

The controller comprises at least one adjusting unit, whereby the adjusting force is used for tilting and axial displacement of the swash plate. The adjusting unit is partly formed by a piston, and the adjusting force shifts the swash plate against the reaction device due to a change in a gas pressure difference between the upper side and the lower side of the piston in the crank chamber. Occur. Said reaction device is formed by a compression spring or, advantageously, by a torsion spring which produces a torque directly on the swash plate, which makes it easier and possibly more economical to assemble than a compression spring. be able to.

Furthermore, the controller may be separate from the piston and may include an adjusting unit for shifting the swash plate. In the case of an adjusting unit which is separate from the piston, the size of the control range can be independent of the operating point. The flow loss between the upper side of the piston and the crank chamber can be reduced. Moreover, the axial piston drive can be operated at low crankcase pressure. The leakage flow of the refrigerant flowing outward from the crank chamber and through the shaft seal is approximately proportional to the pressure in the crank chamber. At low pressures, precise crankcase seals can be eliminated and leakage flow can be smaller. This is especially useful in the case of refrigerants with a high absolute pressure, for which reason a high crankcase pressure is generally required to achieve control via gas pressure differential at the piston. . Furthermore, at low pressures, the air conditioner refrigerant
It is only slightly soluble in the lubricating oil of the capacitor, and as a result a high viscosity can be maintained.

Another way in which the separate regulating unit has a positive effect on the viscosity is to avoid heating the lubricating oil by the gas warmed by the high pressure side of the piston.
With high viscosity, low friction is achieved between the pair of heavily loaded sliding elements of the swash plate and between the piston and the cylinder, which contributes to a long service life and a high level of reliability.

In the case of a regulating unit separate from the piston, no special pressure is required in the crank chamber for control, so that the refrigerant can be guided from the evaporator through the crank chamber into the cylinder. Therefore, the crankcase can be cooled, additional suction chambers above the piston can be prevented from occurring, and thus the space occupied by the entire component can be reduced. Moreover,
Larger volume crankcases are typically available for damping of gas pulsations.

Said adjusting unit is driven by electric, pneumatic or preferably hydraulic means. In the case of hydraulic fluids, an axial piston drive is created which is able to achieve advantageous damping of vibrations and is particularly vibration-insensitive. The adjusting unit can act directly on the swash plate with torque and / or with axial adjustment forces. The adjusting unit with axial action can be sealed particularly easily and can be constructed economically. In the case of the adjusting unit that torques the swash plate, the control torque acts directly on the direction of rotational movement of the swash plate, as a result of which the swash plate can be tilted and axially displaced with a small control torque. A small and space-saving adjustment unit is achieved.

The hydraulic regulating unit is supplied with oil compressed by a hydraulic unit which is independent of the medium delivered by the piston; for example a hydraulic unit already present in the motor vehicle for this purpose. It can be used to advantage. Then, additional components can be eliminated and a large range of control independent of the operating point of the axial piston control can be obtained. Moreover, there is no need to build up pressure for control when the axial piston drive starts up with a minimum tilt angle of eg 2 °. It is possible to enable a no-load start of the axial piston drive device, and for example, it becomes possible to easily start the internal combustion engine that powers the axial piston drive device.

In the case of an oil separator connected downstream of the condenser, good heat transfer to the heat exchanger can be ensured on the high pressure side, and high efficiency of the air conditioner can be achieved. it can. Furthermore, the oil separator can obtain a particularly good use if it supplies compressed oil to the hydraulic regulating unit. Pressure is applied to the oil from the oil separator at the operating point. If a large amount of displacement is required, the oil separator pressure is high; if only a small amount of displacement is required, the oil separator pressure is low.

In one embodiment, it is proposed to connect a hydraulic regulating unit via a drain to the crankcase, which is used by the oil separator and the regulating unit to deliver lubricating oil to the crankcase. This is a particularly beneficial arrangement in some cases. In this process, the flow from the oil separator to the control unit and / or the drain from the control unit to the crankcase can be controllable. The uncontrollable part is advantageously formed by the throttle.

Description of Typical Embodiments FIG. 1 shows an axial piston drive for an automotive air conditioner that functions as a condenser. The axial piston drive comprises a drive shaft 10 having a bearing seat 14 for a swash plate 16 mounted at a first tilt angle 22 (FIG. 2) with respect to a longitudinal direction 20. Crank chamber 24
When located in the inner bearing (14), the swash plate 16 is seated in a bearing bore 30 which is inclined at a second angle 28 with respect to a vertical line 26 of the swash plate 16. Regarding the driving operation, the hemispherical hinge yoke 78,
Through 80, 82, 86, 88, 90, 92, the swash plate 16 is guided into the cylinders 36, 38, 40, 42 (FIGS. 3 and 4) by the four pistons 4.
4,46,48,50. To absorb tensile and compressive loads,
Each piston 44, 46, 48, 50 has two hinge yokes 78, 80, 8
2, 84, 86, 88, 90, 92, hinge yokes 78, 80, 82,
One of 84, 86, 88, 90, 92 is the piston 44, 46, 48, 50.
The swash plate 16 is connected to the bearing surface 96 of the swash plate 16 such that the other hinge yoke contacts the bearing surface 94 of the swash plate 16 facing away from the piston. The hinge yokes 78, 80, 82, 84, 86, 88, 90, 92 all have their radial movements superimposed through their planes along the bearing surfaces 94, 96 of the swash plate 16. It moves at a circumferential velocity, which results in an elliptical orbit. Hinge yoke 78, 80, 82, 84, 86, 88, 90, 9
The two circular surfaces seat on the spherically shaped bearings 98, 100, 102, 104, 106, 108, 110, 112 of the pistons 44, 46, 48, 50, inside which they are relatively movable during operation. There is a small relative movement.

In order to be able to continuously adjust the piston stroke and thus the output of the axial piston drive, the swash plate 16 comprises a controller 3
It is formed so that it can rotate on the bearing seat 14 within an angle range according to 2. When the bearing seat 14 and the bearing bore 30 are tilted in the same direction, the sum of the tilt angles 22, 28 is the maximum effective tilt angle 52 (FIG. 2); if the bearing seat 14 and the bearing bore 30 are in the opposite directions. If tilted, the tilt angles 22 and 28 are subtracted, resulting in a minimum effective tilt angle of 5
4 (FIG. 4). The minimum effective tilt angle 54 is approximately 2 ° to ensure that the pressure is increased when the axial piston drive is started.

According to the present invention, the axial movement motion 56 of the swash plate 16 in the direction toward the pistons 44, 46, 48, 50 is superposed on the rotational movement from the maximum effective inclination angle 52 to the minimum effective inclination angle 54. On the other hand, the pistons 44, 46, 48 are required for the rotational movement from the minimum effective inclination angle 54 to the maximum effective inclination angle 52.
, 50 axial stroke motions 116 of the swash plate 16 in the directions away from each other are superimposed (FIGS. 1-4). The swash plate 16 is connected to the drive shaft 10 by a sled 58 that produces complementary stroke motions 56, 116 from the rotational motion of the swash plate 16. The sled 58 is formed integrally with the drive shaft 10 and has a pitch that is equal to that of the swash plate 16
When it rotates at 0 °, it is displaced axially by a distance equal to half the maximum piston stroke 60 and the top dead center 114 of the pistons 44, 46, 48, 50 remains in the same place in the cylinder track. Is set (FIGS. 2 and 4). The stroke motions 56, 116 and the rotational motion of the swash plate 16 are limited by the stoppers 120, 122 mounted on the drive shaft 10, so that the drive shaft 10 is attached to the axial piston driving device by the lid 162 and the housing. 1
The shaft 64 is axially supported by a thrust bearing 160 and a thrust washer 168. In the radial direction, the drive shaft 10 is fixed to the lid portion 162 and the housing 164 via two radial bearings 166.

The controller 32 comprises an adjusting unit which is partly constituted by pistons 44, 46, 48, 50. Pistons 44, 46, 48 in the crank chamber 24,
Due to fluctuations in the gas pressure differential between the upper side 118 of 50 and the lower side of pistons 44, 46, 48, 50, for a groove or control valve not shown here in detail, the adjusting force is against the reaction mechanism. It occurs to displace the swash plate 16 (FIG. 1). The reaction mechanism is composed of four compression stress torsion springs 62, 64, 66, 68.
Formed by. The torsion springs 62, 64, 66, 68 are supported against the stops 120, 122 of the swash plate 16 and act on said swash plate via stops not shown here in detail. When the swash plate 16 shifts from the maximum effective tilt angle 52 to the minimum effective tilt angle 54, the compressive stress of the torsion springs 62, 64, 66, 68 increases. Swash plate 16
The compressive stress of the torsion springs 62, 64, 66, 68 decreases as the shift from the minimum effective tilt angle 54 to the maximum effective tilt angle 52. Maximum and minimum effective tilt angle 5
Between 2, 54, the swash plate 16 can be continuously adjusted to any desired tilt angle. The swash plate 16 is displaced along a tilted central axis so that the swash plate is slightly eccentric when in the pole position. This imbalance in the pole position can be advantageously avoided by providing a compensation.

FIG. 8 shows a part of the variant according to FIG. 1 with respect to the drive shaft 170. On the drive shaft 170, the sleeve 178 is mounted so as to be axially displaceable and rotationally fixed. The sleeve 178 includes a bearing seat 14 on which a swash plate 174 having a bearing hole 30 is rotatably mounted. The swash plate 174 includes an anti-friction bearing 18
A nut 1 that is axially and radially supported by a sleeve 178 via 2, 184, 186 and is connected to a drive shaft 170 by a screw thread 172.
It is connected to 80 by a coupling 176. With regard to the regulatory action, the essential aspects are clear from the description of the exemplary embodiments in FIGS. The big difference is that the swash plate 174 can be mounted particularly easily,
Further, by appropriately forming the sleeve 178, the center of gravity of the component to be displaced can be guided along the axis of the shaft.

FIG. 5 shows a hydraulic adjustment unit 7 which is a separate body from the pistons 44, 46, 48 and 50.
3 shows an axial piston drive with a controller 34 comprising zero. In the exemplary embodiments shown herein, substantially identical components are essentially identified by the same reference numeral. The adjusting unit 70 includes a housing 124.
A wheel having two vanes 128, 130, 126 supported by
Combined with the two vanes 132, 134 on the housing 124, the four chambers 136,
138, 140, 142 are formed. To rotate the swash plate 18 on the drive shaft 12, the two chambers 142, 138 are routed through the axial and radial bores 144, 146 of the drive shaft 12 and through the radial bore 148 of the wheel 126. Receive high pressure oil pressure. Since the wheel 126 is mounted on the drive shaft 12, the housing 124 can rotate with respect to the wheel 126, exerting a torque on the swash plate 18 via the joint element 150, and by the compressive stress torsion springs 66, 68. The swash plate 18 is displaced against the biasing force. The joint element 150 meshes with the recess 152 of the swash plate 18 and can be axially shifted with respect to the swash plate 18 and abuts the swash plate 18 over the entire range of displacement.

The oil compressed by the oil separator 72 provided on the downstream side of the cylinders 36, 38, 40, 42 is supplied to the adjusting unit 70 via the inflow portion 76, and the adjusting unit 70 drains. It is connected to the crank chamber 24 by 74 (FIG. 7). The refrigerant separated from the oil, as indicated by arrow 154,
It is sent from the oil separator 72 to the low pressure side of the air conditioner. An inflow portion 76 extending from the oil separator 72 to the adjustment unit 70, and the crank chamber 24 from the adjustment unit 70.
Both drains 74 extending to are controllable by valves 156 and 158. Further, the valve 156 or 158 can be replaced by a fixed throttle.

[Brief description of drawings]

Additional advantages will be apparent from the following description of the drawings, which illustrates exemplary embodiments of the invention. The drawings, description and claims contain many features of association. One of ordinary skill in the art will be able to consider individual features and combine them into other beneficial combinations. This drawing shows:

FIG. 1 is an axial piston drive having a piston at the end of its stroke in cross section.

[Fig. 2]   2 is a cross section taken along line II-II in FIG. 1.

FIG. 3 is an axial piston drive according to FIG. 1 with the piston at the end of its stroke in cross section.

[Figure 4]   4 is a cross section taken along line IV-IV in FIG. 3.

[Figure 5]   It is an axial piston drive which has a hydraulic adjustment unit.

[Figure 6]   FIG. 6 is a sectional view taken along line VI-VI of FIG. 5.

[Figure 7]   It is the schematic of the form of hydraulic control.

[Figure 8]   It is a part of the modification according to FIG.

[Explanation of symbols]

10 Drive Shaft 12 Drive Shaft 14 Bearing Seat 16 Swash Plate 18 Swash Plate 20 Longitudinal Direction 22 Inclination Angle 24 Crank Chamber 26 Vertical Line 28 Inclination Angle 30 Bearing Bore 32 Controller 34 Controller 36 Cylinder 38 Cylinder 40 Cylinder 42 Cylinder 44 Piston 46 Piston 48 Piston 50 Piston 52 Inclination angle 54 Inclination angle 56 Stroke operation 58 Thread 60 Piston stroke 62 Torsion spring 64 Torsion spring 66 Torsion spring 68 Torsion spring 70 Adjustment unit 72 Oil separator 74 Drain 76 Inlet 78 Hinge yoke 80 Hinge yoke 82 Hinge yoke 84 Hinge yoke 86 Hinge yoke 88 Hinge yoke 90 Hinge yoke 92 Hinge 94 bearing surface 96 bearing surface 98 bearing 100 bearing 102 bearing 104 bearing 106 bearing 108 bearing 110 bearing 112 bearing 114 top dead center 116 stroke action 118 upper side 120 stopper 122 stopper 124 housing 126 wheel 128 vane 130 vane 132 vane 134 Vanes 136 Chambers 138 Chambers 140 Chambers 142 Chambers 144 Bore Holes 146 Bore Holes 148 Bore Holes 150 Joint Elements 152 Recesses 154 Arrows 156 Valves 158 Valves 160 Thrust Bearings 162 Lids 164 Housings 166 Bearings 168 Thrust Washers 17 Two Shafts 17 17 176 Coupling 1 8 sleeve 180 nut 182 anti-friction bearing 184 anti-friction bearing 186 anti-friction bearings

[Procedure for Amendment] Submission for translation of Article 34 Amendment of Patent Cooperation Treaty

[Submission date] October 9, 2001 (2001.10.9)

[Procedure Amendment 1]

[Document name to be amended] Statement

[Name of item to be corrected] Claim 1

[Correction method] Change

[Contents of correction]

[Procedure Amendment 2]

[Document name to be amended] Statement

[Name of item to be corrected] 0002

[Correction method] Change

[Contents of correction]

[0002] Such an axial piston drive device is known for example US3,304,886 or al. Further, the Achish Yarupisuton drive having a continuously adjustable piston stroke, especially air conditioning system of a motor vehicle, it is also known that may especially be used as a refrigerant condenser.

─────────────────────────────────────────────────── ─── Continued front page    (81) Designated countries EP (AT, BE, CH, CY, DE, DK, ES, FI, FR, GB, GR, IE, I T, LU, MC, NL, PT, SE), OA (BF, BJ , CF, CG, CI, CM, GA, GN, GW, ML, MR, NE, SN, TD, TG), AP (GH, GM, K E, LS, MW, MZ, SD, SL, SZ, TZ, UG , ZW), EA (AM, AZ, BY, KG, KZ, MD, RU, TJ, TM), AE, AG, AL, AM, AT, AU, AZ, BA, BB, BG, BR, BY, BZ, C A, CH, CN, CR, CU, CZ, DK, DM, DZ , EE, ES, FI, GB, GD, GE, GH, GM, HR, HU, ID, IL, IN, IS, JP, KE, K G, KP, KR, KZ, LC, LK, LR, LS, LT , LU, LV, MA, MD, MG, MK, MN, MW, MX, MZ, NO, NZ, PL, PT, RO, RU, S D, SE, SG, SI, SK, SL, TJ, TM, TR , TT, TZ, UA, UG, US, UZ, VN, YU, ZA, ZW F term (reference) 3H075 AA00 BB02 CC12 CC30 CC36                       DA03 DA04 DB03 DB04 DB24                 3H076 AA06 BB31 BB43 CC07 CC12                       CC19 CC28 CC31 [Continued summary] Axial direction of the swash plate (16, 18, 174) Stroke operation (56) is overlapped and minimum effective tilt Time from tilt angle (54) to maximum effective tilt angle (52) When rolling, separate from the piston (44, 46, 48, 50) Stroke of the swash plate in the direction It is proposed to superimpose the operation (116).

Claims (11)

[Claims] 1. A drive shaft (10, 12, 170) and a longitudinal direction (20).
And a swash plate (16, 18, 174) provided on the bearing seat (14) located at a first tilt angle (22) with respect to the swash plate (16, 18, 174) in the crank chamber. (16,18
, 174) of the swash plate (16, 18, 17) supported with a bearing bore (30) that inclines at a second inclination angle (28) with respect to a vertical line (26).
4) is rotatable in a certain angular range by the controller (32, 34) to adjust the piston stroke, and additionally the cylinder (36, 38, 40, 4)
2) at least one piston (44,46,48,50) movably mounted and drivingly connected to the swash plate (16,18,174)
In an axial piston drive device having a continuously movable piston stroke, the rotary motion from the maximum effective inclination angle (52) to the minimum effective inclination angle (54),
The swash plate (in the direction toward the pistons (44, 46, 48, 50)
16, 18, 174) axial stroke motions (56) are superposed, and pistons (44, 46, 48, 50) are used for rotational motion from the minimum effective tilt angle (54) to the maximum effective tilt angle (52). Axial piston drive, characterized in that the axial stroke movement (116) of the swash plate in the direction away from is superimposed. 2. The swash plate (16, 18, 174) is driven by a screw thread (58, 172) that produces an axial stroke motion of a complementary angle from the rotational motion of the swash plate (16, 18, 174). (1
0, 12, 170) operatively connected to the axial piston drive of claim 1. 3. The axial piston drive device according to claim 2, wherein the screw thread (58, 172) is formed integrally with the drive shaft (10, 12, 170). 4. The swash plate () when rotated at an angle of 180 °
Axial piston drive according to any one of the preceding claims, characterized in that 16, 18, 174) are axially shifted by a distance of half the maximum piston stroke (60). 5. The axial piston drive device according to claim 2, wherein the swash plate (174) is rotatably seated on a sleeve (178) that slides in the axial direction. . 6. The controller (32) includes the swash plate (1).
6,174) at least one compressive stress torsion spring (62,64,
66, 68). An axial piston drive as claimed in any one of the preceding claims, characterized in that it comprises a reaction force mechanism having (66, 68). 7. The controller (34) comprises the pistons (44, 46,
50) An axial piston drive according to any one of the preceding claims, characterized in that it comprises an adjusting unit (70) separate from 50). 8. The axial piston drive according to claim 7, wherein the adjusting unit (70) is hydraulically driven. 9. The hydraulic pressure adjusting unit (70) comprises pistons (44, 46, 48).
, 50) supplies compressed oil by means of a hydraulic unit independent of the medium delivered by the axial piston drive. 10. The hydraulic pressure adjusting unit (70) includes the cylinders (36, 3).
9. The axial piston drive device according to claim 8, wherein compressed oil is supplied by an oil separator (72) provided on the downstream side of 8, 40, 42). 11. The hydraulic pressure adjusting unit (70) is connected to a crank chamber (24) via a drain (74), and an inflow portion (70) from the oil separator (72) to the adjusting unit (70). Axial piston arrangement according to claim 10, characterized in that the drain (74) from the adjusting unit (70) and / or the adjusting unit (70) to the crank chamber (24) is controllable.