WO2008077596A1 - Hydrostatic axial piston engine - Google Patents

Hydrostatic axial piston engine Download PDF

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Publication number
WO2008077596A1
WO2008077596A1 PCT/EP2007/011303 EP2007011303W WO2008077596A1 WO 2008077596 A1 WO2008077596 A1 WO 2008077596A1 EP 2007011303 W EP2007011303 W EP 2007011303W WO 2008077596 A1 WO2008077596 A1 WO 2008077596A1
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WO
WIPO (PCT)
Prior art keywords
piston
adjusting
actuating
machine
hydrostatic
Prior art date
Application number
PCT/EP2007/011303
Other languages
German (de)
French (fr)
Inventor
Josef Beck
Martin Zug
Original Assignee
Robert Bosch Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to DE200610061145 priority Critical patent/DE102006061145A1/en
Priority to DE102006061145.4 priority
Application filed by Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2008077596A1 publication Critical patent/WO2008077596A1/en

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26Control
    • F04B1/30Control of machines or pumps with rotary cylinder blocks
    • F04B1/32Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
    • F04B1/324Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate

Abstract

The invention relates to a hydrostatic axial piston engine with a cylinder drum (106) which is mounted rotatably in a housing (103). Longitudinally displaceable working pistons (111) are disposed in cylinder boreholes (110) in the cylinder drum (106). The working pistons (111) are connected movably to sliding blocks (149) and are supported on a face (116) of an inclined disk (115). Furthermore, the hydrostatic axial piston engine (101 has a control piston (126) which interacts with the inclined disk (115) for adjusting an angle of inclination of the face (116) with respect to an axis of rotation (144) in the cylinder drum (106). The control piston (126) is supported over a control piston sliding block (149') on the face (116) of the inclined disk (115) in order to exert a regulating force on the inclined disk (115).

Description

 Hydrostatic axial piston machine

The invention relates to a hydrostatic

Axial piston machine with the features of the preamble of claim 1.

In axial piston machines, a cylinder drum is rotatably arranged. The cylinder drum is rotatably connected to a drive shaft. In the cylinder drum are arranged distributed on a circumferential circle several cylinder bores. In the cylinder bores in each case a working piston is arranged longitudinally displaceable. To a hub of the in the

To reach cylinder bores arranged working piston, the working pistons are supported on a running surface of a swash plate. The tread is arranged obliquely with respect to the axis of rotation of the cylinder drum.

In adjustable axial piston machines, the inclination of this tread is adjustable. For this purpose, the tread is arranged on a swash plate, which is often designed as a pivoting cradle. Such axial piston machine is known from DE 199 49 169 Al. In order to adjust the inclination angle of the tread with respect to the axis of rotation of the axial piston machine, an adjusting device is arranged there in a housing opening. The adjusting device comprises an actuating piston which cooperates with the swash plate for tilt adjustment of the swash plate. For this purpose, a ball head is formed on the actuating piston, which engages in a spherical recess on the swash plate. By thus formed joint connection between the actuating piston and the swash plate is an inclination of the two elements to each other, as it automatically occurs in an adjustment of the angle of the swash plate, possible. The receiving opening for receiving the adjusting device in the housing of Axial piston machine is provided, is arranged obliquely with respect to the axis of rotation of the cylinder drum.

In the known from DE 199 49 169 Al axial piston machine, it is disadvantageous that a special articulation of the swash plate is formed with the adjusting piston of the adjusting device. The fixed distance of the point of application of the actuating piston on the swash plate also requires a lateral motion compensation, with a change in inclination of the swash plate. This considerably increases the complexity of manufacturing the axial piston machine. In addition, the oblique arrangement of the adjusting device in a recess of the housing is disadvantageous because the forces that are required to adjust the swash plate, are considerable. Thus, the load must be transferred through the housing, which is why high-quality housing material must be used. This increases the cost of the entire axial piston machine.

It is therefore an object of the present invention to provide an axial piston machine which allows an improved adjustment of the inclination angle of the swash plate and which is simple and inexpensive to manufacture.

The object is achieved by the axial piston machine according to the invention with the features of claim 1.

The axial piston machine according to the invention has a housing in which a cylindrical drum is rotatably mounted. In the cylinder drum several cylinder recesses are arranged, in each of which a working piston is arranged longitudinally displaceable. The working piston are supported by means of a respective sliding shoe on a running surface of a swash plate. The connection between the working piston and the sliding shoes is designed to be movable. Furthermore, an actuating piston is provided, which with the swash plate for adjusting an inclination angle of the tread with respect to the axis of rotation of the cylinder drum cooperates. According to the invention, the adjusting piston is connected to a steep piston guide shoe, which is supported on the running face of the swash plate so as to generate a setting force on the swash plate. The construction according to the invention has the advantage that only one tread is to be formed on the part of the swashplate. This tread is usually designed as a simple flat surface. By means of the sliding shoe, therefore, a thrust force can be exerted by the adjusting piston on the running surface of the swash plate in a simple manner. At the same time, the support point of the actuating piston sliding shoe can automatically adjust in the radial direction on the running surface during an adjusting movement. A special design of a hinge connection between the swash plate and the actuator piston is not required.

In the dependent claims advantageous developments of the axial piston according to the invention are carried out.

Preferably, a ball joint is arranged between the control piston and the Stellkolbengleitschuh. By connecting the actuator piston with the

Stellkolbengleitschuh a ball joint, it is achieved that the mounting position of the actuating piston or the Stellkolbengleitschuhs with respect to a rotation of the actuating piston or the Stellkolbengleitschuhs is irrelevant. It is particularly advantageous if the adjusting piston and the working piston have an identical geometry. This eliminates a separate production of the actuating piston. Due to the increased number of identical parts within the axial piston machine can thus be achieved a significant cost savings. In particular, it is also advantageous to design the actuating piston sliding shoe identically with the sliding shoes of the working piston. It is particularly preferred if both the adjusting piston and the working piston are identical the Stellkolbengleitschuh with the shoes of the working piston has an identical geometry.

Furthermore, it is preferred if the actuating piston is arranged in an actuator housing and is longitudinally displaceable along a longitudinal axis of the actuator housing. The longitudinal axis of the actuator housing extends at least approximately parallel to a rotational axis of the cylinder drum. By such an approximately parallel

Arrangement of the required space in the lateral direction is reduced with respect to the axis of rotation of the cylinder drum. In the actuator housing, a stepped recess is preferably arranged. In the stepped recess, the adjusting piston and a valve piston of a valve for actuating a control pressure acting on the actuating piston are arranged axially successively. In the actuator housing thus a single multi-stage bore can be provided, in which all components that are needed to produce an actuating movement of the swash plate and thus a stroke volume of the axial piston machine, are arranged. In particular, a return spring can be provided within the actuator housing, with the help of the position of the

Control piston is returned to the valve piston. By such a return, a control signal corresponding, for example, proportional, adjustment of the displacement volume of the hydrostatic piston engine is possible.

It is particularly preferred if the return spring is identical to the pressure springs used in the cylinder bores of the cylinder drum. By using the already required Andrückfedern in the

Adjustment of turn, the same part of the same proportion is increased within the axial piston and thus achieved a cost reduction. Furthermore, it is preferred if the

Actuator housing is mounted in a connection plate of the axial piston machine. In the connection plate, the pressure lines for supplying and removing the conveyed for example by a hydraulic pump pressure medium are arranged. If, therefore, the actuator housing is arranged in the connection plate, it is possible to act on the valve piston arranged in the actuator housing with the pressures required for adjustment over shorter lines or channels. External lines can be omitted, since all channels can be provided within the terminal plate or within the actuator housing. In particular, the assembly is facilitated because the

Connection plate can be pre-assembled together with the adjusting device as an assembly and then inserted after the onset of the engine in the housing of the axial piston machine.

An inventive embodiment of an axial piston machine is shown in the drawing and will be explained in more detail in the following description. Show it:

Fig. 1 is a schematic representation of a hydrostatic axial piston machine with a known adjusting device;

Fig. 2 is a hydraulic circuit diagram for explaining the operation of the adjusting device; and

Fig. 3 is an enlarged view of an axial piston machine according to the invention.

Before an axial piston machine according to the invention is explained in detail with reference to FIG. 3, the basic structure and is first based on Fig. 1 the function of a hydrostatic axial piston machine will be explained.

FIG. 1 shows a hydrostatic axial piston machine 1. The well-known hydrostatic

Axial piston machine 1 has an engine 2, which is arranged in a housing 3. To insert the engine 2 in the housing 3, the housing 3 is open at one end. The open end is closed by a connecting plate 4 after assembly of the engine 2 in the housing 3. At the connection plate 4, the line connections are provided in a manner not shown.

The engine 2 comprises a drive shaft 5 and a cylinder drum 6 rotatably connected therewith. The drive shaft 5 is arranged rotatably together with the cylinder drum 6 in the housing 3.

The drive shaft 5 is rotatably mounted for this purpose at one end of the housing 3 in a first bearing 7. At the opposite end of the drive shaft 5, a second bearing 8 is provided, which is arranged in the illustrated embodiment in the connection plate 4. The drive shaft 5 penetrates with one end 9, the first bearing 7 and the end face of the housing 3 of the hydrostatic axial piston machine first

For the following description, it is assumed that the hydrostatic axial piston machine 1 is an adjustable hydraulic pump 1. The end 9 of the drive shaft 5 is therefore connected to drive the hydraulic pump with a drive motor.

In the cylinder drum 6 are distributed on a circumferential circle arranged a plurality of cylinder bores 10 in the cylinder drum 6. In each cylinder bore 6, a working piston 11 is arranged in each case. The working piston 11 can be displaced along the center axis of the cylinder bore 10 in the longitudinal direction. Of the Working piston 11 is movably connected to a sliding block 12 via a ball joint 13. The shoes 12 of the working piston 11 are supported by a sliding surface on a swash plate 15. The swash plate 15 is executed in the illustrated embodiment as a pivoting cradle which is rotatably mounted in a spherical bearing. On the swash plate 15, a tread 16 is formed on its side facing the cylinder drum 6 as a flat surface.

While in Fig. 1, the tread 16 and the swash plate 15 is shown in its neutral position, which corresponds to a zero flow volume of the hydraulic pump, the working piston 11 are shown in a position which would correspond to a swivel angle α of the swash plate 15.

Upon rotation of the drive shaft 5 rotates due to the rotationally fixed connection and the cylinder drum 6. The shoes 12 are based on the running surface 16 of the swash plate 15 and force the working piston 11 in a lifting movement. In order to prevent the sliding blocks 12 from lifting off the running surface 16 of the swash plate 15 during a suction stroke, a return plate 14 is provided. The retraction plate 14 follows the inclination angle of the swash plate 15 and is mounted on a spherical bearing 17.

For temporary connection of the cylinder bores 10 with the lines of a hydrostatic circuit is a

Control plate 18 is provided. In the control plate 18 control openings 19, 20 are formed, with which the cylinder bores 10 communicate alternately during one revolution of the cylinder drum 6. To the cylinder drum 6 at the mouth side of

Cylinder bores 10 to hold on the control plate 18 in sealing contact, a spring 21 is provided in the interior of the cylinder drum 6. The spring 21 is supported on the one hand on the cylinder drum 6, in this regard For example, a snap ring is arranged as a first spring bearing. A second spring bearing is formed on the opposite side of the spring 21 on the drive shaft 5.

For adjusting the stroke volume of the axial piston machine 1, an adjusting device 22 is provided. The adjusting device 22 is actuated by means of a proportional magnet 23. The proportional solenoid 23 acts in a manner not shown a

Valve piston of the adjusting device 22, which adjusts a force acting on a control piston 26 actuating pressure.

On the adjusting piston 26, a spherical connecting element 24 is formed. This spherical

Connecting element 24 engages in a spherical recess 25, which is arranged on the swash plate 15. The longitudinal axis of the adjusting device 22 includes a non-zero angle with the axis of rotation of the cylinder drum 6 a.

2, a hydraulic circuit is shown, which is provided for adjusting an axial piston machine 1. The hydrostatic axial piston machine 1, which is driven in the case of a hydraulic pump via the drive shaft 5, sucks pressure medium via a suction line 27 from a tank volume 28 at. In the illustrated

Embodiment is shown an arrangement in an open circuit. However, the axial piston machine can also be arranged in a closed circuit. The pressure medium sucked in by the hydrostatic axial piston machine 1 is conveyed into a working line 29 in accordance with the set delivery volume. For adjusting the delivery volume of the hydraulic pump, the adjusting device 22 is provided. The adjusting device 22 comprises, in addition to the adjusting piston 26, a setting pressure control valve 32. The adjusting pressure control valve 32 sets a control pressure acting on the adjusting piston 26. The acting on the actuator piston 26 actuating pressure is taken from the working line 29 via a sampling line 31. The actuating piston 26 is acted upon in one direction by a return spring 33 with a spring force. In a control pressure chamber 35, a return spring 34 is arranged, which acts on a valve piston of the

Partial pressure control valve 32 transmits a dependent of the position of the actuating piston 26 force. The pressure control valve 32 is in the rest position of the actuator 22 in its position shown in FIG. In this position, the extraction line 31 is connected to a control pressure line 36. As a result, in the control pressure chamber 35, the prevailing in the working line 29 pressure. This pressure acts on the actuating piston 26 with his to the control pressure chamber

Pressure chamber 35 oriented piston surface. As a result, the actuating piston 26 is deflected in Fig. 2 to the left. The adjusting piston 26 compresses the restoring spring 33 because of the adjusting movement. During an adjusting movement of the adjusting piston 26 against the force of the return spring 33, the hydrostatic axial piston machine 1 is adjusted in the direction of its minimum delivery volume.

Starting from the specified rest position of the

Control pressure control valve 32, the pitch control valve 32 can be acted upon in the direction of a second end position with a force. This force is e.g. generated by a proportional magnet 23. The force of the proportional magnet 23 acts against the force of

Return spring 34. If now the proportional solenoid 33 is acted upon by a control signal, the valve piston of the control pressure control valve 33 experiences a force in the direction of its second end position. In this second end position, the control pressure line 36 with a

Connecting line 37 connected. The signal pressure control valve 32 is continuously adjustable between these two end positions. During normal operation, the connection line 37 via a safety valve 39 with the tank line 30 connected. In the second end position of the pitch pressure control valve 32, therefore, the control pressure chamber 35 is connected via the connecting line 37 to the tank line 30 and the control pressure chamber 35 is expanded into the tank volume 28. As a result, reduces the force on the piston surface of the actuating piston 26 and the return spring 33 moves the actuator piston 26 so that the hydrostatic axial piston machine 1 is adjusted in the direction of increasing delivery volume.

In order to be able to set a proportional adjusting movement or a proportional delivery volume of the hydrostatic axial piston machine 1, the force of the return spring 34 acts counter to the force of the proportional magnet 23 on the valve piston of the

Partial pressure control valve 32. Thus, a dependent of the respective position of the actuating piston 26 force is exerted on the valve piston of the pressure control valve 32.

The control pressure line 36 is also via a

Bypass line 36 'connected to the connecting line 37. In the bypass line 36 ', a throttle point 38 is arranged. Via the throttle point 38 so that a discharge of pressure medium from the control pressure chamber 35 is made possible, for example, starting from its first end position by acting on the proportional solenoid 23 with a lower control signal, the pressure control valve 32 is slightly adjusted in the direction of its second end position.

The safety valve 39 connects in its rest position, the connecting line 27 in the manner already described with the tank line 30. This rest position is defined by a safety valve spring 40. In the opposite position of the safety valve 39, however, a further connecting line 41 is connected to the connecting line 37. The further connection line 41 branches off from the extraction line 31. In the opposite position of the Safety valve 39 is thus the connecting line 37, the pressure of the working line 29 is supplied. The pressure prevailing in the further connecting line 41 is further supplied via a first measuring line 42 to a measuring surface formed on the safety valve 39. The force acting on the measuring surface hydraulic force acts opposite to the force of the safety valve spring 40. Conversely, in the same direction acts with the safety valve spring 40 to the safety valve 39 via a second measuring line 43, the pressure in the tank line 30th

About the safety valve spring 40, which is designed as an adjustable spring, the opening differential pressure of the safety valve 39 can be adjusted. Will this

Opening pressure exceeded by the pressure difference between the supplied via the first measuring line 42 and the second measuring line 43 pressure, the safety valve 39 is adjusted in the direction of its second end position. With increasing adjustment in

Direction of the second end position increases the pressure in the control pressure chamber 35, even if the pressure control valve 32 is in its second end position. As a result, the actuating piston 26 is moved in Fig. 2 to the left, which has a reduction of the delivery volume result.

FIG. 3 shows an enlarged view of a section of an axial piston machine 101 according to the invention. For the sake of a clearer illustration, the illustration of the elements of the axial piston machine 101 known per se has been dispensed with. For this, the axial piston machine 101 is shown enlarged in the region of the adjusting device 122. With the Fig. 1 matching elements and features are provided with increased by 100 reference numerals.

As already explained with reference to FIG. 1, there are in the cylinder barrel 126 in there attached cylinder bores 110 working piston 111 arranged longitudinally displaceable. The working piston 111 are connected by means of a ball joint 113 with sliding shoes 112. For this purpose, at one end of the working piston 111, which from the cylinder bores 110 of

Cylindrical drum 106 protrudes, a spherical head 147 is formed. This spherical head 147 engages in a spherical recess 148 of the sliding shoe 149. From the opposite side, a recess 146 is introduced into the working piston 111. The recess 146 is preferably listed as a bore, and dimensioned so that a pressure spring 145 can be arranged therein. A lubricating oil bore 150 connects the recess 146 with the head end of the working piston 111. The pressure spring 145 is in the untensioned state longer than the maximum distance between the head end of the bore 146 and the opposite end of the cylinder bore 110. The pressure spring 145 thus exerts a force both on the cylinder drum 106 and the working piston 111 from. Thus, the cylinder drum 106 is held in abutment with the control plate 118. The working piston 111, however, is held together with the slide shoe 149 in contact with the running surface 116 of the swash plate 115.

On the sliding shoe 149, a sliding surface 152 is formed. The sliding surface 152 preferably has at least one lubricating oil groove 151. The Schmierölnut is connected via a connecting bore with the area in the spherical recess 148. That in the

Cylinder bore 110 pressurized fluid is therefore passed through the lubricating oil bore 150 and the connecting hole in the shoe 149 to the Schmierölnut 150 and there provides a hydrostatic relief of the shoe 149. Further, the contact surface between the spherical recess 148 and the spherical head 147th supplied with pressure medium for lubrication. Due to the ball joint-like connection between the shoe 149 and the Spherical head 147 of the working piston 111, the inclination of the sliding surface 147 relative to the longitudinal axis of the working piston 111 can be changed. This ensures that the sliding surface 152 can be adjusted at any possible angular position of the tread 147 relative to the axis of rotation 144 of the cylindrical drum 106. The spherical recess 148 comprises the spherical head 147 so far that between the working piston 111 and the shoe 149 also tensile forces can be transmitted.

To adjust the angle of the tread 116 relative to the axis of rotation 144 of the cylindrical drum 106, the actuator 122 is provided.

To generate an adjusting movement, the adjusting device 122 comprises an actuating piston 126. The actuating piston 126 is identical to the working piston 111. A renewed description of the individual components with respect to the actuating piston 126 is therefore omitted. The actuating piston 126 is connected via an articulated connection 113 'with a Stellkolbengleitschuh 149'. The Stellkolbengleitschuh 149 'corresponds in its construction to the shoe 149, as he was already described in connection with the working piston 111.

Therefore, the Stellkolbengleitschuh 149 'on a sliding surface 152', which is in contact with the tread 116. An actuating force, which is exerted to the left by the actuating piston 126 in FIG. 3, can thus be transmitted to the running surface 116 of the swashplate 115. In the recess 146 of the actuating piston 126, a spring is also arranged. This spring is designed as a return spring 145 '. The return spring 145 'is supported on the one hand at the head-side end of the recess 146' in the actuating piston 126. The opposite end of the feedback spring 145 'is supported on a spring bearing 147. The spring bearing 147 in turn is applied to a first end of a valve piston 158. Thus, a force is exerted on the valve piston 158, which depends both on the position of the valve piston 158 and on the position of the actuating piston 126. Thus, a restoring force is exerted as position information on the actuator piston 158, as has already been explained with reference to the hydraulic circuit diagram of FIG. This force depends on the position of the swashplate 115 and thus on the set delivery volume.

The adjusting device 122 comprises a

Actuator housing 153. The actuator housing 153 is inserted into a recess in the connection plate 104, preferably screwed. The connection plate 104 closes the housing 103 of the hydrostatic axial piston machine 101.

The actuator housing 153 has a stepped recess 154. The stepped recess 154 is designed as a hole and penetrates the

Actuator housing 153 along a longitudinal axis 162 of the actuator housing 153. The longitudinal axis 162 of the actuator housing 163 is preferably oriented parallel to the axis of rotation 144 of the cylinder drum 106. Depending on the exact structural design of the connection plate 104, however, a slight deviation from the parallelism may occur by a few degrees.

In the swash plate 115 facing the end of

Actuator housing 153, a bushing 155 is inserted. The bushing 155 is formed substantially pot-shaped, wherein in the bottom of the bushing 155, a through hole is provided. The passage opening of the bushing 155 is arranged approximately in the region of the first end of the valve piston 158 and dimensioned so that the spring bearing 157 can pass. The bushing 145 is held in the swash plate end of the adjuster housing 122 by means of a snap ring 160. The actuating piston 126 and the valve piston 158 are axially offset from one another in the actuator housing 153. The adjusting piston 126 is in operative connection with the valve piston 158 via the return spring 145 '. Ring grooves 159, 160 are formed on the valve piston 158. By means of the annular grooves 159,

160 is a function of the position of the valve piston 158 relative to the actuator housing 153 a

Connection between a removal channel 131 and the control pressure chamber 135 produced. Depending on the position of the valve piston 158, the annular groove 160 connects the extraction channel 131 with the connection 161 hidden in FIG. 3 by the valve piston 158. The connection

161 is connected via a likewise not shown channel with the control pressure chamber 135. When the valve piston 158 is acted upon by an axial force by the proportional magnet 123, on the other hand, the second annular groove 159 is brought into a position in which the connection 161 is connected to the connection channel 137 in a flow-through manner. The connection channel 137 is formed in the terminal plate 104.

The axial force, which is generated by a proportional magnet 123, is transmitted by means of a plunger 159 to the end remote from the spring bearing 157 of the valve piston 158. In the region of the end of the valve piston 158 facing away from the spring bearing 157, a rest position spring 161 is arranged. The rest position spring 161 is supported on the one hand on the

Verstellvorrichtungsgehäuse 163 and on the other hand on a collar 165 from.

By forming the adjusting device 122 under

Use of parts which are also used as a working piston 111 and as a sliding block 149, a considerable simplification of the hydrostatic axial piston machine 101 is achieved. In particular, the production becomes cheaper, because a separate parts production can be avoided for the actuator piston. In particular, the production of the swash plate 115 is greatly simplified. In contrast to the known from the prior art axial piston machine only a uniformly flat tread 116 must be generated, which extends over the entire circumference of the swash plate 115. Not only is the plurality of working pistons 111 supported on their running surface 116 via their sliding shoes 149, but also a positioning force of the adjusting piston 126 can be transmitted to the running surface 116 by means of the actuating piston sliding shoe 149 '. In order to enable a provision of the swash plate 115, a return spring 133 is disposed on the side facing away from the tread 116 side of the swash plate 115. The return spring 133 acts on the swash plate 115 against the actuating force of the actuating piston 126 with a restoring force.

If the pressure chamber 135 of the adjusting device 122 is therefore relieved at the corresponding position of the valve piston 128 in the tank volume 28, the swash plate 115 is brought back into its neutral position due to the force of the return spring 133. In this neutral position, the hydrostatic axial piston engine 101 is adjusted to its maximum delivery volume. Thus, in a pressureless system due to the neutral position of the hydrostatic axial piston 101 initially a pressure build-up in the working line 29. This pressure build-up is then also supplied to the pressure chamber 135 due to the rest position of the valve piston 158. As a result, an equilibrium of forces arises at the valve piston 158. The balance of forces exists between the force acting on the valve piston 158 force of the feedback spring 145 and the same direction of the force of the rest position spring 163 and the opposing force of the proportional solenoid 123, which acts on the plunger 159 via the plunger 159. The supply of the sliding surface 152 'of the

Stellkolbengleitschuhs 159 'is also comparable to the already described lubrication of the sliding surface 152 of the shoe 149. For this purpose, the sliding surface 152' is connected via a connecting bore and a lubricating oil hole in the actuating piston 126 with the control pressure chamber 135. Thus, from the pressure acting in the control pressure chamber 135, a lubricating film is generated both between the spherical head of the control piston 126 and on the sliding surface 152 '. An exact one

Pivoting angle adjustment is achieved by reducing the friction.

The invention is not limited to the illustrated embodiment. So can the

Axial piston machine can also be designed as a hydraulic motor and in particular individual features of the invention can be combined.

Claims

claims
1. Hydrostatic axial piston machine with a rotatably mounted in a housing (103) cylindrical drum (106), in the longitudinally displaceable working piston (111) in
Cylinder bores (110) are arranged, wherein the working piston (111) with sliding shoes (149) are movably connected and the working piston (111) via the sliding blocks (149 ') on a running surface (116) of a swash plate (115) supported, and with an actuating piston (126) which cooperates with the swashplate (115) for setting an inclination angle of the running surface (116) with respect to an axis of rotation (144) of the cylindrical drum (106), characterized in that the actuating piston (126) is provided with an actuating piston sliding shoe (149 '). ) is connected and acted on the Stellkolbengleitschuh (149 '), the running surface (116) of the swash plate (116) with a force.
Second hydrostatic axial piston machine according to claim 1, characterized in that the adjusting piston (126) and the Stellkolbengleitschuh (149 ') are interconnected by a ball joint.
3. Hydrostatic axial piston machine according to claim 1 or
2, characterized in that the adjusting piston (126) and the working piston (111) have an identical geometry.
4. Hydrostatic axial piston machine according to one of claims 1 to 3, characterized in that the Stellkolbengleitschuh (149 ') and the sliding blocks (149) of the working piston (111) have an identical geometry.
5. Hydrostatic axial piston machine according to one of claims 1 to 4, characterized in that the adjusting piston (126) in one
Actuator housing (153) is longitudinally displaceable along a longitudinal axis (162) of the actuator housing (153) and the longitudinal axis (162) of the actuator housing (153) extends at least approximately parallel to the axis of rotation (144) of the cylindrical drum (106).
6. Hydrostatic axial piston machine according to claim 5, characterized in that the actuating piston (126) in a stepped recess (154) of the actuator housing (153) is arranged and offset in the axial direction to the actuating piston (126) has a valve piston (158) in the Stufenausnehmung ( 154) is arranged.
7. Hydrostatic axial piston machine according to claim 5 or 6, characterized in that for returning a position information of the actuating piston (126) a return spring (145 ') is provided which on the one hand on the actuating piston (126) and on the other hand on a valve piston (158) is supported ,
8. Hydrostatic piston machine according to claim 7, characterized in that the return spring (145 ') is identical with in the cylinder recesses (110) inserted Andrückfedern (145).
9. Hydrostatic piston machine according to one of claims 1 to 8, characterized in that the adjusting device housing (153) in a
Connection plate (104) of the axial piston machine (101) is attached.
PCT/EP2007/011303 2006-12-22 2007-12-20 Hydrostatic axial piston engine WO2008077596A1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE200610061145 DE102006061145A1 (en) 2006-12-22 2006-12-22 Hydrostatic axial piston machine
DE102006061145.4 2006-12-22

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US12/520,749 US20090288552A1 (en) 2006-12-22 2007-12-20 Hydrostatic axial piston machine
CN 200780047856 CN101595304B (en) 2006-12-22 2007-12-20 Hydrostatic axial piston engine
EP20070857026 EP2092192B1 (en) 2006-12-22 2007-12-20 Hydrostatic axial piston engine
AT07857026T AT529635T (en) 2006-12-22 2007-12-20 Hydrostatic axial piston machine

Publications (1)

Publication Number Publication Date
WO2008077596A1 true WO2008077596A1 (en) 2008-07-03

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Application Number Title Priority Date Filing Date
PCT/EP2007/011303 WO2008077596A1 (en) 2006-12-22 2007-12-20 Hydrostatic axial piston engine

Country Status (6)

Country Link
US (1) US20090288552A1 (en)
EP (1) EP2092192B1 (en)
CN (1) CN101595304B (en)
AT (1) AT529635T (en)
DE (1) DE102006061145A1 (en)
WO (1) WO2008077596A1 (en)

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009006909B4 (en) 2009-01-30 2019-09-12 Robert Bosch Gmbh Axial piston machine with reduced actuating pressure pulsation
DE102011113533A1 (en) 2011-09-15 2013-03-21 Robert Bosch Gmbh Hydrostatic axial piston machine user for swash plate construction, has cylinder piston unit whose axial section is encompassed with spring
DE102011113534A1 (en) 2011-09-15 2013-03-21 Robert Bosch Gmbh Hydraulic piston machine
DE102012015503A1 (en) * 2012-08-04 2014-02-06 Robert Bosch Gmbh Hydrostatic axial piston machine
DE102012021320A1 (en) * 2012-10-31 2014-04-30 Robert Bosch Gmbh Adjustment device for a hydrostatic piston engine and hydrostatic piston engine with such adjustment
DE102012022201A1 (en) * 2012-11-13 2014-05-15 Robert Bosch Gmbh Adjusting device for an axial piston machine and hydraulic machine with such an adjusting device
DE102012022997A1 (en) * 2012-11-24 2014-05-28 Robert Bosch Gmbh Adjustment device for a hydraulic machine and hydraulic axial piston machine
DE102013220229A1 (en) * 2013-10-08 2015-04-09 Robert Bosch Gmbh Swash plate machine
CN103573616B (en) * 2013-11-08 2016-03-02 无锡威孚精密机械制造有限责任公司 The variable cylinder structure of plunger pump
DE102014211194A1 (en) * 2014-06-12 2015-12-17 Robert Bosch Gmbh Hydrostatic axial piston machine in swash plate design and fan with a hydrostatic axial piston machine
EP3056729B1 (en) 2015-02-11 2019-03-27 Danfoss A/S Axial piston machine
KR20180071372A (en) * 2015-11-15 2018-06-27 이턴 인텔리전트 파워 리미티드 Hydraulic Pump Control System
DE102015121882A1 (en) * 2015-11-19 2017-05-24 Linde Hydraulics Gmbh & Co. Kg Hydrostatic axial piston machine

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1073216A (en) * 1962-11-21 1967-06-21 F W Baggett & Co Ltd Improvements relating to swash plate pumps and motors
US3753627A (en) * 1971-04-09 1973-08-21 E Ward Pump bypass liquid control
US4379389A (en) * 1980-09-12 1983-04-12 Caterpillar Tractor Co. Horsepower consumption control for variable displacement pumps
JPS5990781A (en) * 1982-11-16 1984-05-25 Hitachi Constr Mach Co Ltd Axial piston type rotary machine employing fluid pressure
FR2793850A1 (en) * 1999-05-20 2000-11-24 Renault Motor vehicle hydromechanical transmission system has toothed rings on crown wheel of first epicycloid gear train and output shaft gear
DE19949169A1 (en) * 1999-10-12 2001-04-26 Brueninghaus Hydromatik Gmbh Adjustment device
EP1628028A2 (en) * 2004-08-16 2006-02-22 Eaton Corporation Hydraulic drive system

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1548095A (en) * 1976-05-10 1979-07-04 Bryce J M Apparatus and method for attaching a wire to a supporting post
DE10351473B3 (en) * 2003-11-04 2005-07-21 Brueninghaus Hydromatik Gmbh axial piston
DE10360452B3 (en) * 2003-12-22 2005-09-08 Brueninghaus Hydromatik Gmbh Axial piston machine with fixable sliding block on the swashplate

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1073216A (en) * 1962-11-21 1967-06-21 F W Baggett & Co Ltd Improvements relating to swash plate pumps and motors
US3753627A (en) * 1971-04-09 1973-08-21 E Ward Pump bypass liquid control
US4379389A (en) * 1980-09-12 1983-04-12 Caterpillar Tractor Co. Horsepower consumption control for variable displacement pumps
JPS5990781A (en) * 1982-11-16 1984-05-25 Hitachi Constr Mach Co Ltd Axial piston type rotary machine employing fluid pressure
FR2793850A1 (en) * 1999-05-20 2000-11-24 Renault Motor vehicle hydromechanical transmission system has toothed rings on crown wheel of first epicycloid gear train and output shaft gear
DE19949169A1 (en) * 1999-10-12 2001-04-26 Brueninghaus Hydromatik Gmbh Adjustment device
EP1628028A2 (en) * 2004-08-16 2006-02-22 Eaton Corporation Hydraulic drive system

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EP2092192A1 (en) 2009-08-26
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CN101595304A (en) 2009-12-02
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US20090288552A1 (en) 2009-11-26
DE102006061145A1 (en) 2008-06-26

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