DE102010053804A1 - piston engine - Google Patents

Abstract

Disclosed is a hydrostatic piston machine with a first and a second group of cylinder-piston units. The pistons are - preferably via a common disc - coupled to a drive shaft and rotate with it. The stroke between the cylinders and the pistons of the first group depends on the position of a first adjustable pivoting cradle and the stroke between the cylinders and the pistons of the second group depends on the position of a second adjustable pivoting cradle. The two swivel cradles or their swivel angles are coupled to one another, preferably mechanically, hydraulically, pneumatically or electrically, and their common adjustment is synchronized.

Description

The invention relates to a piston engine according to the preamble of patent claim 1.

Axial piston engines having a plurality of cylinder-piston units are known from the prior art in which, in order to generate a stroke of the pistons in the respective cylinders, an oblique position of a component coupled to the cylinders relative to a component of the axial piston engine coupled to the pistons is required. Furthermore, the cylinder-piston units must rotate (relative to a housing).

In this case, axial piston machines are known according to the oblique axle principle, in which the pistons are coupled to a disk of a shaft, while the cylinders are formed in a cylinder drum inclined with respect to the shaft. Since the cylinder drum rotates synchronously with the shaft during operation of the axial piston machine, the pistons rotate accordingly.

Alternatively, axial piston machines are known according to the swash plate principle, in which the pistons are coupled to a swash plate, which is inclined with respect to a shaft. The cylinders are formed in a cylindrical drum which is concentric with the shaft. The cylinder drum and the pistons rotate synchronously with the shaft during operation of the axial piston machine. Because of the necessary relative movement of the pistons relative to the swash plate, feet of the pistons are received in piston shoes that slide over the swash plate.

On the website of the company INNAS www.innas.com and in the EP 1 705 372 A1 Another piston engine is shown in a floating-cup technology (FCT), which has two groups of cylinder-piston units. In contrast to the above-described axial piston machines according to the swashplate principle, the cylinders are supported in the form of sleeves via a drum disk on a respective pivoting cradle, while the pistons are fastened to a common drum or disk. The disc is concentric with the shaft and rotatably mounted on the shaft. Since the disc with the piston rotates synchronously with the shaft during operation of the piston engine, the cylinder sleeves accordingly revolve. There are kidney-shaped control slots in the two swivel housings. To seal these control slots to the interior of the machine housing down the drum discs are necessary, which have individual matched to the cylinder sleeves and stroking the control slots breakthroughs and rotate with the cylinder-piston units. The pivoting balances are designed to be adjustable in their angle, so that the stroke of the cylinder-piston units and thus the flow rate of the machine can be changed.

A disadvantage of such piston engines of the latter type with two groups of cylinder-piston units is that the control of a volume flow, as required for example for the realization of hydraulic control circuits, requires an increased effort.

In contrast, the invention is based on the object to provide a piston engine in a floating Cup or Tilting Cup Technology (FCT or TCT) with two groups of cylinder-piston units, with which hydraulic control circuits are realized with less effort can.

This object is achieved by a piston engine having the features of patent claim 1.

The hydrostatic piston engine according to the invention has a first and a second group of cylinder sleeve-piston units. The pistons are - preferably via a common disc - coupled to a drive shaft and run with this. The cylinders are formed by cylinder sleeves. The stroke between the cylinder sleeves and the piston of the first group depends on the position of a first adjustable pivoting cradle and the stroke between the cylinder sleeves and the piston of the second group from the position of a second adjustable pivoting cradle. The two pivoting pivots and their pivoting angles are - preferably mechanically, hydraulically, pneumatically or electrically - coupled to each other and synchronized in their adjustment, so aligned in path and time to each other. Thus, a piston machine of FCT or TCT type with two groups of cylinder-piston units is created with which hydraulic control circuits can be realized.

Further advantageous embodiments of the invention are described in the dependent claims.

In a particularly preferred application, the two groups of cylinder-piston units, the two pivoting pivots are arranged substantially mirror-inverted to a plane perpendicular to the drive shaft central plane of the piston engine.

In a preferred development, a pin or bolt is attached to the two pivoting pivots directly or via a respective connecting element, for example via a lever arm. The two pins or bolts are guided in a running approximately parallel to the drive shaft common backdrop, and a distance of the gate to Drive shaft is adjustable in particular via a control cylinder. Then, the synchronous adjustment can be done mechanically by a linear adjustment.

In another preferred embodiment, a spindle nut is coupled to the two pivoting pivots each directly or via a connecting element, for example a lever arm, wherein the two spindle nuts are coupled via a spindle extending approximately parallel to the drive shaft. This can be powered by a motor. Then, the synchronous adjustment can be done mechanically by a rotational adjustment.

In another preferred embodiment, a gear segment is attached to the two pivoting pivots each directly or via a connecting element, for example via a lever arm, wherein the two gear segments mesh with each other. Thus, a device-technically simple mechanical synchronous coupling is created.

In another preferred embodiment of the first pivoting cradle directly or via a connecting element -. B. a lever arm - a first linear actuator coupled, while the second pivoting cradle directly or via a connecting element -. B. a lever arm - a second linear actuator is coupled. The two linear actuators can be electric linear motors, piezo actuators, pneumatic actuators or hydraulic actuators.

In this case, the first linear actuator may be a first actuating cylinder, while the second linear actuator is a second actuating cylinder. For a hydraulic adjustment is created.

It is preferred if for the coupling of the two actuating cylinder of this invention, a common hydraulic flow divider is connected upstream.

It is preferred if the hydraulic flow divider is formed by two constant-displacement pumps, of which the two adjusting cylinders can be supplied, and when the two constant-displacement pumps are coupled to one another via a connecting shaft. Then, the synchronous adjustment can be done hydraulically by a rotational adjustment movement of the connecting shaft. The connecting shaft can serve as a common drive shaft.

Alternatively, it is preferred if the hydraulic flow divider is formed by a stepped cylinder with stepped piston, from which the two adjusting cylinders can be supplied. An annular space and a cylindrical space of the stepped cylinder are each connected to one of the two actuating cylinders. An annular space bounding the annular space of the stepped piston and a cylindrical space defining end face of the stepped piston are the same size. Then, the synchronous adjustment can be done hydraulically by a linear adjustment movement of the stepped piston.

In the case of an electrical or electronic coupling, a control valve, whose respective actuator can be adjusted by a common electronic control unit as a function of a respective displacement sensor, can be connected in each case upstream of the two actuating cylinders. The two displacement sensors are coupled to a respective actuating piston of the actuating cylinder. This also allows an asynchronous adjustment of the piston engine or the stroke of its two cylinder-piston units.

In order to equalize an introduction of force for adjusting the pivoting weigh it is preferred if the first pivoting cradle - preferably via an additional first lever arm - a first additional actuating cylinder is articulated to a first actuating cylinder opposite side of the drive shaft, while corresponding to the second pivoting cradle - preferably via an additional second lever arm - a second additional actuating cylinder is articulated on a second actuating cylinder opposite side of the drive shaft. The effective directions of the respective actuating cylinder and the respective additional actuating cylinder are directed in a same pivoting direction of the corresponding pivoting cradle.

For device-technically simple pivoting back of the two pivoting pivots may be provided on the two adjusting cylinders and / or on the two additional adjusting cylinders return springs.

In a preferred development, the first actuating cylinder and the first additional actuating cylinder can be supplied via a first line pair from a common first pump, wherein the second actuating cylinder and the second additional actuating cylinder can be supplied via a second line pair from a common second pump. For coupling according to the invention, the two pumps are coupled to one another via a connecting shaft. As a result, each pivoting cradle is pivoted via an introduction of a pair of forces, which leads in particular to the high-pressure side pivot bearing for a reduction in losses due to leakage. The connecting shaft can serve as a common drive shaft.

For "pivoting" internal coupling of the respective actuating cylinder with the respective additional actuating cylinder via the supply thereof, a first flow divider can be provided in the first line pair be arranged while in the second line pair, a second flow divider is arranged. Preferably, the flow dividers are two pumps coupled to each other via a connecting shaft.

In another preferred embodiment of the piston engine according to the invention, the first pivoting cradle via a first rotary actuator and the second pivoting cradle is pivotable via a second rotary actuator. The two rotary actuators are coupled to each other. The actuators can be designed electrically, piezoelectrically, pneumatically or hydraulically.

It is particularly preferred if the first rotary actuator is a first hydraulic swing-wing motor and the second rotary actuator is a second hydraulic swing-wing motor. If the two swing-wing motors each have a working line acting in the direction of increasing the pivoting angle and a working line acting in the direction of reducing the pivoting angle, the coupling of the swivel-weighing adjustment according to the invention can take place via two flow dividers. The one flow divider is connected to the two acting in the direction of enlargement of the pivot angle working lines and the other flow divider with the two acting in the direction of a reduction of the pivot angle working lines. Preferably, the two flow dividers are each two pumps coupled to each other via a connecting shaft.

The inventive coupling of the two SchenkWiegen can also be done via a drive shaft obliquely employed coupling rod, which is hinged to the first pivoting cradle via a first joint and on the second pivoting cradle via a second joint. The two joints are each articulated on different sides of the drive shaft to the respective pivoting cradle. It can be additionally provided a second coupling rod for generating a symmetry and as a gain.

The inventive coupling of the two Schenkwiegen can also be done via two obliquely stretched and crossed on the drive shaft and crossed pliable traction means, which are each attached to the first pivoting cradle at a first attachment point and the second pivoting cradle at a second attachment point. The two attachment points of the two traction means are attached to different sides of the drive shaft to the respective pivoting cradle.

The two pivoting pivots can also be arranged approximately parallel to one another and coupled to one another via a coupling rod arranged essentially parallel to the drive shaft.

In the following, various embodiments of the invention will be described in detail with reference to FIGS. Show it:

1 a first embodiment of the piston engine according to the invention in a schematic side view;

2 A second embodiment of the piston machine according to the invention in a schematic side view;

3 a third embodiment of the piston engine according to the invention in a schematic side view;

4 A fourth embodiment of the piston engine according to the invention in a schematic side view;

5 a fifth embodiment of the piston engine according to the invention in a schematic side view;

6 a sixth embodiment of the piston engine according to the invention in a schematic side view;

7 a seventh embodiment of the piston engine according to the invention in a schematic side view;

8th an eighth embodiment of the piston pump according to the invention in a schematic side view;

9 a ninth embodiment of the piston engine according to the invention in a schematic side view;

10 A tenth embodiment of the piston machine according to the invention in a schematic side view; and

11 an eleventh embodiment of the piston engine according to the invention in a schematic side view.

1 shows a first embodiment of the piston engine according to the invention in a schematic side view. The piston engine has a continuous drive shaft, from the in 1 only two end sections 1a . 1b are shown, each via a rolling bearing 2a . 2 B are stored.

On the outer circumference of the drive shaft are two Schwenkwiegen 4a . 4b arranged on which mutually facing swash plates 6a . 6b are arranged. To every swashplate 6a . 6b is a variety of cylinder sleeves over their respective front and via a drum disc rotating with the cylinder sleeves 7a . 7b having a number of fluid passages corresponding to the number of adjacent cylinder sleeves. It is in 1 only an exemplary cylinder sleeve 8a shown.

The Schwenkwiegen 4a . 4b with the swash plates 6a . 6b and the cylinder sleeves coupled thereto 8a are mirror images of a middle plane 10 and arranged obliquely with respect to the drive shaft of the piston engine. The middle level 10 is perpendicular to the drive shaft and is in 1 shown in a "cut" representation as a dashed line.

In the area of the middle level 10 is a (in 1 not shown) rotatably connected to the drive shaft disc (see 742 out 8th ). At the two approximately circular opposing surfaces of the disc a plurality of pistons are mounted, of which 1 only one piston, for example 12a is shown.

When the piston engine according to the invention is used as a pump, it is at one of the end portions 1a . 1b driven by the drive shaft. About the (not shown) disc, the pistons 12a taken on an orbit around the drive shaft and in turn take the cylinder sleeves 8a With. Due to the inclination of the two swash plates 6a . 6b lead the cylinder sleeves 8a a lifting movement relative to the respective piston 12a out.

In every swing cradle 4a . 4b two approximately kidney-shaped slots are provided, one of which is connected to a high-pressure channel HDa, HDb and the other with a low-pressure channel NDa, NDb. The two high-pressure channels HDa, HDb lead to a common (not shown) high-pressure port of the piston engine, while the two low-pressure channels NDa, NDb are connected to a common (not shown) low-pressure port of the piston engine. In another embodiment, the two high-pressure channels HDa and HDb can also remain separate and serve the pressure medium supply of each other hydraulic consumers. The same applies to the low-pressure channels.

For further details of the piston engine shown is on the document EP 1 705 372 A1 directed.

The adjustment or adjustment of the swivel angle of the two swash plates 6a . 6b (over the two Schwenkwiegen 4a . 4b ) is synchronized according to the invention, to which in the first embodiment, a mechanical coupling is provided which via a differential cylinder 14 is driven. From the two Schwenkwiegen 4a . 4b each extends a lever arm 16a . 16b towards the middle level 10 , where am to the middle level 10 adjacent end portion of each lever arm 16a . 16b a cone 18a . 18b is attached. The two cones 18a . 18b also extend in mirror symmetry to the middle plane 10 and perpendicular to the drawing plane. They are together in a good setting 20 taken up, approximately parallel to the drive shaft on both sides of the middle plane 10 and mirror-symmetric to this extends. The scenery 20 is according to the arrow on the differential cylinder 14 movable in a direction perpendicular to the drive shaft. This move the two pins 18a . 18b either towards or away from each other and so adjust over the respective lever arm 16a . 16b and about the respective pivoting cradle 4a . 4b the two swash plates 6a . 6b synchronous.

2 shows a second embodiment of a piston engine according to the invention in a schematic side view. The drive shaft correspond to the two end sections 1a . 1b and the two rolling bearings 2a . 2 B as well as the two Schwenkwiegen 4a . 4b with the two swash plates 6a . 6b and with the two drum discs 7a . 7b and the four channels HDa, HDb, NDa, NDb according to those of the first embodiment 1 , Furthermore, the second embodiment also has two groups of cylinder-piston units, of which in 1 only one cylinder-piston unit 8a . 12a is shown by way of example.

The adjusting device of the second embodiment has two at the respective pivoting cradle 4a . 4b fixed lever arms 116a . 116b that are (in 2 ) from a respective axis of rotation 119a . 119b extend upward and mirror-symmetrical to the middle plane 10 are arranged. From the respective swing cradle 4a . 4b remote end portions of the two lever arms 116a . 116b are rotatable with a respective spindle nut 118a . 118b connected. The two spindle nuts 118a . 118b are on a common spindle 120 arranged, which is fixed axially by means of suitable storage. The spindle 120 runs approximately parallel to the drive shaft and can be driven by an electric motor 114 be rotated in both directions. By opposing threaded sections on the spindle 120 in the areas of the respective spindle nut 118a . 118b These are achieved by a rotation of the spindle 120 either towards or away from each other. As a result, the coupling according to the invention is the adjustment of the two swash plates 6a . 6b given in a mechanical way.

3 shows a third embodiment of the piston engine according to the invention in a schematic side view. The drive shaft correspond to the two end sections 1a . 1b and the two rolling bearings 2a . 2 B , the two Schwenkwiegen 4a . 4b with the two swash plates 6a . 6b and the two drum discs 7a . 7b , the four channels HDa, HDb, NDa, NDb and the two lever arms 16a . 16b those of the first embodiment according to 1 ,

Furthermore, the third embodiment also has two groups of cylinder-piston units, of which in 1 only one cylinder-piston unit 8a . 12a is shown by way of example.

At the two mutually facing end portions of the two lever arms 16a . 16b is each a gear segment 218a . 218b arranged. The two gear segments 218a . 218b are mirror-symmetric with respect to the middle plane 10 arranged and combed with each other. This is a mechanical coupling of the two swash plates 6a . 6b given, the pivot angle of the two swash plates 6a . 6b can be adjusted by a (not shown) adjusting device.

4 shows a fourth embodiment of the piston engine according to the invention in a schematic side view. The drive shaft correspond to the two end sections 1a . 1b and the two rolling bearings 2a . 2 B , the two Schwenkwiegen 4a . 4b with the two swash plates 6a . 6b and the two drum discs 7a . 7b , the four channels HDa, HDb, NDa, NDb according to those of the first embodiment 1 , Furthermore, the fourth embodiment also has two groups of cylinder-piston units, of which in 1 only one cylinder-piston unit 8a . 12a is shown by way of example.

For coupling according to the invention, the pivot angle of the two swash plates 6a . 6b is a coupling rod according to the fourth embodiment 320 provided, which has a first joint 318a to the first pivoting cradle 4a and a second joint 318b to the second pivoting cradle 4b is coupled. The coupling rod 320 runs obliquely to the drive shaft and oblique to the middle plane 10 , Here is the first joint 318a in an area of the first pivoting cradle 4a arranged, the comparatively large distance to one with respect to the middle level 10 mirror image area of the second pivoting cradle 4b has, while the second joint 318b at an area of the second pivoting cradle 4b is arranged, which is a comparatively small distance to one with respect to the middle plane 10 mirror image area of the first pivoting cradle 4a Has. Thus, the two joints 318a . 318b on different sides of the two Schwenkwiegen 4a . 4b arranged with respect to the drive shaft.

About a (not shown) adjusting the coupling rod 320 or one of the two Schwenkwiegen 4a . 4b moved, with the two swash plates of 6a . 6b are mechanically synchronized.

5 shows a fifth embodiment of the piston engine according to the invention in a schematic side view. The drive shaft correspond to the two end sections 1a . 1b and the two rolling bearings 2a . 2 B , the two Schwenkwiegen 4a . 4b with the two swash plates 6a . 6b and the two control plates 7a . 7b , the four channels HDa, HDb, NDa, NDb and the two lever arms 116a . 116b those of the second embodiment according to 2 , At the Schwenkwiegen 4a . 4b are accordingly the two lever arms 116a . 116b attached, which (in 5 ) from the respective axis of rotation 119a . 119b extend upward and thereby mirror-symmetrical to the middle plane 10 are arranged. Here are the of the respective pivoting cradle 4a . 4b remote end portions of the lever arms 116a . 116b via a respective rotary push joint with a piston rod of a respective actuating cylinder 422a . 422b connected. The effective directions of the two actuating cylinders 422a . 422b are directed parallel to the drive shaft to the outside, whereby by such a movement, the pivot angle of the two swash plates 6a . 6b be enlarged. To reset the actuating cylinder 422a . 422b and thus to reduce the tilt angle of the two swash plates 6a . 6b Return springs are provided.

For synchronization according to the invention of the hydraulic adjustment is each actuating cylinder 422a . 422b a constant pump 424a . 424b assigned, via which the respective actuating cylinder 422a . 422b can be supplied with pressure medium. The two constant pumps have 424a . 424b a connecting shaft 426 , on the two their delivery volumes and thus the adjustment of the two actuating cylinder 422a . 422b are hydraulically synchronized.

6 shows a sixth embodiment of the piston engine according to the invention in a schematic side view. The sixth embodiment largely corresponds to the fifth embodiment according to 5 , Therefore, only the difference of the sixth embodiment from the fifth embodiment will be explained in the following: The uniform synchronous supply of the two actuating cylinders 422a . 422b with pressure medium via a step cylinder 528 with corresponding stepped piston 530 , This is an annulus 532 and a cylindrical space 534 formed, with one the annulus 532 limiting annular surface of the stepped piston 530 and a cylindrical space 534 limiting face of the stepped piston 530 are the same size. The annulus 532 of the stage cylinder 528 is at the first actuating cylinder 422a connected while the cylindrical room 534 of the stage cylinder 528 to the second actuating cylinder 422b connected.

During a movement of the stepped piston (in 6 ) to the right this performs a Verdrängerhub. The from the annulus 532 in the first actuating cylinder 422a delivered pressure medium quantity corresponds to that amount of pressure medium, which from the cylindrical space 534 to the second actuating cylinder 422b is encouraged. Even so are the Verstellhübe the two actuating cylinders 422a . 422b and thus the tilt angle of the two swash plates 6a . 6b always the same size.

7 shows a seventh embodiment of the inventive piston machine in a schematic side view. The seventh embodiment corresponds largely to the fifth embodiment according to 5 and the sixth embodiment according to 6 , so that in the following only the differences from the fifth and the sixth embodiment will be explained: The two actuating cylinder 422a . 422b be via a respective 3/2-way valve, as a control valve 636a . 636b serves, either connected to high pressure P or relieved to low pressure T. When connecting the two control valves 636a . 636b At high pressure, the two actuating cylinders 422a . 422b moved outward, causing the tilt angle of the two swash plates 6a . 6b be enlarged.

The positions of the two piston rods of the actuating cylinder 422a . 422b from a respective displacement sensor 638a . 638b recorded and to a control unit 640 transmitted. From the control unit 640 become the control valves 636a . 636b adjusted via respective actuators.

The inventive coupling of the adjustment angle of the two swash plates 6a . 6b takes place in the seventh embodiment in the form of an electro-hydraulic control of the adjustment.

8th shows an eighth embodiment of the piston pump according to the invention in a schematic representation. As with the previous embodiments is perpendicular to the drive shaft 1 a concentric disc 742 arranged. As with the previous embodiments are on both opposite sides of the disc 742 On the circumference distributed pistons fastened, of which in 8th for example, only one piston at a time 12a . 12b is shown. These dive each in a cylinder sleeve 8a . 8b one. The cylinder sleeves are 8a the first group of cylinder-piston units 8a . 12a over the first drum disc 7a to the first swash plate 6a coupled, while correspondingly the cylinder sleeves 8b the second group of cylinder-piston units 8b . 12b over the second drum disc 7b to the second swash plate 6b are coupled. The two swash plates 6a . 6b stand in normal operation obliquely to the drive shaft 1 and to the disc 742 ,

In the eighth embodiment, the disc is 742 and thus indirectly also the drive shaft 1 over two radial bearings 744a . 744b supported on a (not shown) housing of the piston engine.

In the eighth embodiment, the two swash plates 6a . 6b about their respective swivel cradle 704a . 704b aligned approximately parallel to one another. This parallel position remains even with a pivoting of the two swash plates 6a . 6b obtained, wherein the synchronization of the pivoting according to the invention in this embodiment takes place mechanically. This is a coupling rod 720 provided, which is approximately parallel to the drive shaft 1 runs. The coupling rod 720 is about perpendicular to the drive shaft 1 extending connecting sections 721a . 721b articulated with the two pivoting weigh 704a . 704b connected. By a (in 8th ) adjusting device, not shown, the coupling rod 720 parallel to the drive shaft 1 moved, causing the tilt angle of the two swash plates 6a . 6b be adjusted synchronously according to the invention.

9 shows a ninth embodiment of the piston engine according to the invention in a schematic side view. This corresponds to the drive shaft 1 with the two end sections 1a . 1b and with the two rolling bearings 2a . 2 B , the two Schwenkwiegen 4a . 4b with the swash plates 6a . 6b and with the (in 9 not shown) drum discs 7a . 7b and the four channels HDa, HDb, NDa, NDb according to those of the first embodiment 1 , For adjusting the respective swivel angle of the two swash plates 6a . 6b is on each pivot cradle 4a . 4b a swing-wing motor 846a . 846B arranged. The two swing-wing motors 846a . 846B can each be driven in two directions, whereby a reduction or increase in the respective pivot angle and thus the displacement or delivery volume of the piston engine according to the invention is adjustable.

Two displacement machines (constant pumps / motors or power dividers) 424a . 424b whose delivery volume flows via a connecting shaft 426 are evened, provide the two swing-wing motors 846a . 846B according to the invention in synchronism with pressure medium. As a result, the swivel angle of the two swash plates 6a . 6b synchronously enlarged.

Two further displacement machines (constant pumps / motors or also flow dividers) 824a . 824b , whose flow rates also over a connecting shaft 826 are evened, provide the two swing-wing motors 846a . 846B with pressure medium, this supply to a pivoting back of the swash plates 6a . 6b leads.

10 shows a tenth embodiment of the piston engine according to the invention in a lateral schematic representation. This embodiment has all the components of the fifth embodiment according to 5 , so that in the following only the components beyond are explained: To improve the introduction of a pivoting torque in the respective pivoting cradle 4a . 4b around the respective axis of rotation 119a . 119b is on each pivot cradle 4a . 4b an additional lever arm 917a . 917b attached to the corresponding additional actuating cylinder 923a . 923b is articulated. The two additional lever arms 917a . 917b , the two additional actuating cylinders 923a . 923b and their return springs are identical to those of the fifth embodiment according to 5 , The additional actuating cylinders 923a . 923b and their return springs are parallel to the drive shaft 1 aligned. Here are the two additional lever arms 917a . 917b and the two additional actuating cylinders 923a . 923b related to the drive shaft 1 opposite the two lever arms 116a . 116b or with respect to the two adjusting cylinders 422a . 422b arranged. The two additional actuating cylinders 923a . 923b be in the same way with pressure medium from the respective associated displacement machines (constant pumps / motors or power splitters) 424a . 424b supplied, as the two actuating cylinder 422a . 422b and also act in the direction of increasing the swing angle of the reciprocating engine.

11 shows an eleventh embodiment of the piston engine according to the invention in a lateral schematic representation. Since the eleventh embodiment largely corresponds to the tenth embodiment, only the differences from the tenth embodiment will be described below 10 explains: Between the first constant pump 424a and the first two actuating cylinders 422a . 923a is to equalize the torque introduction, a first flow divider 1050a . 1052a arranged. Corresponding is also between the second constant pump 424b and the two second cylinders she supplied 422b . 923b a flow divider 1050b . 1052b arranged. The two displacement machines 424a and 424b Work here primarily as Constantpumpen, which is why they are also referred to above. The two flow dividers each consist of two constant motors 1050a . 1050b , which have a respective connecting shaft 1052a . 1052b mechanically coupled to each other.

The connection waves 426 . 826 the embodiments according to 9 . 10 and 11 can also drive the two constant pumps coupled to it 424a . 424b respectively. 824a . 824b serve.

Disclosed is a hydrostatic piston engine having a first and a second group of cylinder-piston units. The pistons are - preferably via a common disc - coupled to a drive shaft and run with this. The cylinders of the first group are coupled to a first swash plate, while the cylinders of the second group are coupled to a second swash plate. The first oblique disk is pivotable via a first pivoting cradle and the second inclined disk correspondingly via a second pivoting cradle. The two pivoting pivots or their pivoting angles are - preferably mechanically, hydraulically, pneumatically or electrically - coupled to each other and synchronized.

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• EP 1705372 A1 [0005, 0048]

Claims (20)

Hydrostatic piston engine having a first and a second group of cylinder-piston units ( 8a . 12a . 8b . 12b ), wherein the cylinders of cylinder sleeves ( 8a . 8b ) are formed, and wherein the plunging into the cylinder sleeves ( 12a . 12b ) to a drive shaft ( 1 ) and rotate with this, and wherein the stroke between the cylinder sleeves ( 8a ) and the piston ( 12a ) of the first group of the position of a first adjustable pivoting cradle ( 4a ) and the stroke between the cylinder sleeves ( 8b ) and the piston ( 12b ) of the second group of the position of a second adjustable pivoting cradle ( 4b ), characterized in that the two pivoting ( 4a . 4b ) are coupled together and synchronized in their adjustment. Piston engine according to claim 1, wherein the two groups of cylinder-piston units ( 8a . 12a . 8b . 12b ) and the two pivoting ( 4a . 4b ) is substantially mirror-inverted to a perpendicular to the drive shaft ( 1 ) arranged middle level ( 10 ) of the piston engine are arranged. Piston engine according to claim 2, wherein at the two pivoting ( 4a . 4b ) each directly or via a connecting element ( 16a . 16b ) a pin ( 18a . 18b ) or bolt is fastened, wherein the two pins ( 18a . 18b ) or bolts in an approximately parallel to the drive shaft ( 1 ) running common scenery ( 20 ) are guided, and wherein a distance of the backdrop ( 20 ) to the drive shaft ( 1 ) is adjustable. Piston engine according to claim 2, wherein the two pivoting pivots ( 4a . 4b ) each directly or via a respective connecting element ( 116a . 116b ) a spindle nut ( 118a . 118b ), and wherein the two spindle nuts ( 118a . 118b ) over an approximately parallel to the drive shaft ( 1 ) running spindle ( 120 ) are coupled. Piston engine according to claim 3, wherein at the two pivoting pivots ( 4a . 4b ) each directly or via a connecting element ( 16a . 16b ) a gear segment ( 218a . 218b ), and wherein the two gear segments ( 218a . 218b ) comb each other. Piston engine according to claim 1, wherein a first linear actuator is coupled to the first pivoting cradle directly or via a connecting element, and wherein a second linear actuator is coupled to the second pivoting cradle directly or via a connecting element. Piston engine according to claim 6, wherein the first linear actuator, a first actuating cylinder ( 422a ), and wherein the second linear actuator is a second actuating cylinder ( 422b ). Piston engine according to claim 7, wherein the two actuating cylinders ( 422a . 422b ) a common hydraulic flow divider is connected upstream. Piston engine according to claim 8, wherein the hydraulic flow divider of two constant displacement machines ( 424a . 424b ) is formed, of which the two actuating cylinder ( 422a . 422b ), and wherein the two constant displacement machines ( 424a . 424b ) via a connecting shaft ( 426 ) are coupled together. Piston engine according to claim 8, wherein the hydraulic flow divider of a step cylinder ( 528 ) with stepped piston ( 530 ) is formed, of which the two actuating cylinder ( 422a . 422b ), and wherein an annulus ( 532 ) and a cylindrical space ( 534 ) of the step cylinder ( 528 ) each with one of the actuating cylinder ( 422a . 422b ) and wherein one of the annulus ( 532 ) limiting annular surface of the stepped piston ( 530 ) and a cylindrical space ( 534 ) limiting end face of the stepped piston ( 530 ) are the same size. Piston engine according to claim 7, wherein the two actuating cylinders ( 422a . 422b ) each a control valve ( 636a . 636b ), the respective actuator of a common electronic control unit ( 640 ) in dependence of a respective displacement sensor ( 638a . 638b ) or tilt angle sensor is adjustable, wherein the two displacement sensors ( 638a . 638b ) to a respective actuating piston of the actuating cylinder ( 422a . 422b ) are coupled. Piston engine according to claim 7, wherein the first pivoting cradle ( 4a ) a first additional actuating cylinder ( 923a ) on a first actuating cylinder ( 422a ) opposite side of the drive shaft ( 1 ), and wherein the second pivoting cradle ( 4b ) a second additional actuating cylinder ( 923b ) on a second actuating cylinder ( 422b ) opposite side of the drive shaft ( 1 ), and wherein effective directions of the respective actuating cylinder ( 422a . 422b ) and the respective additional actuating cylinder ( 923a . 923b ) in a same pivoting direction of the respective pivoting cradle ( 4a . 4b ) are directed. Piston engine according to claim 12, wherein on the two actuating cylinders ( 422a . 422b ) or on the two additional actuating cylinders ( 923a . 923b ) Return springs are provided. Piston engine according to claim 12, wherein the first actuating cylinder ( 422a ) and the first additional actuating cylinder ( 923a ) via a first line pair of a common first constant pump ( 424a ), and wherein the second Adjusting cylinder ( 422b ) and the second additional actuating cylinder ( 923b ) via a second line pair of a common second constant pump ( 424b ) and the two pumps ( 424a . 424b ) via a connecting shaft ( 426 ) are coupled together. Piston engine according to claim 14, wherein in the first line pair, a first flow divider ( 1050a . 1052a ) is arranged, and wherein in the second line pair, a second flow divider ( 1050b . 1052b ) is arranged. Piston engine according to claim 1, wherein the first pivoting cradle is pivotable via a first rotary actuator, and wherein the second pivoting cradle is pivotable via a second rotary actuator, and wherein the two rotary actuators are coupled to each other. A piston engine according to claim 16, wherein the first rotary actuator is a first hydraulic swing-wing motor ( 846a ), and wherein the second rotary actuator is a second hydraulic swing-wing motor ( 846B ), and wherein the two swing-wing motors ( 846a . 846B ) each having an acting in the direction of enlargement of the pivot angle working line and acting in the direction of reduction of the pivot angle working line, and wherein the two acting in the direction of enlargement of the pivot angle working lines and the two acting in the direction of reduction of the pivot angle working lines each have a flow divider ( 424a . 424b . 426 . 824a . 824b . 826 ) are coupled. Piston engine according to claim 2, wherein one to the drive shaft ( 1 ) obliquely employed coupling rod ( 320 ) via a first joint ( 318a ) at the first pivoting cradle ( 4a ) and a second joint ( 318b ) on the second pivoting cradle ( 4b ), and wherein the two joints ( 318a . 318b ) each on different sides of the drive shaft ( 1 ) are arranged. Piston engine according to claim 2, wherein two with respect to the drive shaft obliquely stretched and crossed pliable traction means are respectively attached to the first pivoting cradle at a first attachment point and the second pivoting cradle at a second attachment point, and wherein the two attachment points of each traction means on different sides of the drive shaft are attached. Piston engine according to claim 1, wherein the two pivoting ( 704a . 704b ) arranged approximately parallel to one another and over a substantially parallel to the drive shaft ( 1 ) arranged coupling rod ( 720 ) are coupled together.

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