JP2008540924A - Hydraulic piston machine based on floating cup principle - Google Patents

Abstract

Disclosed is a hydraulic piston machine based on the principle of a floating cup that can be used more freely because it is discharged separately into two power transmission groups.
The invention relates to a hydraulic piston machine (1) based on the principle of a floating cup and comprising a first swash plate (16) and a second swash plate (17). The first cylinder drum unit (11, 14) is supported by the first swash plate, and the second cylinder drum unit ( 13 , 15) is supported by the second swash plate (17). The first piston group (10) and the second piston group (12) are fixedly connected to the drive shaft (5) of the hydraulic piston machine (1). The first piston group (10) engages with the cylinder recess of the first cylinder drum unit (11, 14), and the second piston group (12) engages with the cylinder recess of the second cylinder drum unit ( 13 , 15). The first and second cylinder chambers respectively defined by the piston group (10, 12) and the cylinder drum unit (11, 14; 13 , 15) can be connected to the first and second fluid circuits, respectively. The drive shaft of the first cylinder drum unit (11, 14) and / or the drive shaft of the second cylinder drum unit ( 13 , 15) can be adjusted independently of each other.
[Selection] Figure 1

Description

  The present invention relates to a hydraulic piston machine based on the principle of a floating cup.

  Hydraulic piston machines based on the floating cup principle improve the friction loss of conventional piston machines. A piston machine that operates on the principle of a floating cup is disclosed in US Pat. The hydraulic piston machine has a drive shaft arranged in a housing, and the piston is arranged firmly connected to the drive shaft via a support plate. Each drum plate is provided with a cylinder, and similarly connected to the drive shaft so as to be freely rotatable with respect to each piston group protruding in the opposite direction from the support. Since the rotation axis of the drum plate is inclined to the same degree with respect to the drive shaft, the first and second group pistons arranged in the cylinder reciprocate with respect to the cylinder. Since the rotation axes of the two drum plates are similarly inclined in the opposite directions, the same level of force acts on the piston in the axial direction.

  A power transmission group consisting of a piston, a cylinder, and a drum plate is formed on both sides of the support plate, and discharged to a common fluid circuit. For this reason, the high pressure side of the two drum units and the low pressure side of the two drum units are connected to each other by the housing of the piston machine. The two drum plates are each supported by a swash plate, and the swash plate can be adjusted together.

  The hydraulic piston machine of Patent Document 1 has a drawback that both piston groups only discharge to a common fluid circuit, and the adjustment of the two swash plates corresponds to each other. Such adjustment common to the two swash plates is required in the hydraulic piston machine disclosed in Patent Document 1 in order to adapt the axial force acting on both piston groups.

  However, such a piston machine cannot be used in a hydraulic system having two separate circuits that are supplied independently of each other. For example, two separate fluid circuits can be provided and used as a plurality of pumps, or the discharge capacity can be set individually for the first piston group and the second piston group by independently adjusting the two swash plates. I can't.

International Publication No. 03/058035 Pamphlet

  An object of the present invention is to provide a hydraulic piston machine based on the principle of a floating cup that can be used more freely by separating and discharging into two power transmission groups.

  The object of the invention is achieved by a hydraulic piston machine having the features of claims 1 and 2 of the invention.

  The hydraulic piston machine of the present invention has two power transmission groups. The first power transmission group includes a first swash plate that supports the first cylinder drum unit. The first piston group is disposed in the cylinder recess of the first cylinder drum unit, and these pistons are firmly and rotatably connected to the drive shaft of the hydraulic piston machine. The second power transmission group includes a second swash plate that supports the second cylinder drum unit. Similarly, the cylinder recess with which the second piston group engages is disposed in the second cylinder drum unit. Similarly, the second piston group is firmly and rotatably connected to the drive shaft of the hydraulic piston machine. A first cylinder chamber group is formed in the cylinder recess of the first cylinder drum unit by the first piston group. A second cylinder chamber group is formed in the cylinder recess of the second cylinder drum unit by the second piston group. The first cylinder chamber group and the second cylinder chamber group are respectively connected to separate fluid circuits in order to obtain two discharge flows of the pressure medium. As a result, the hydraulic piston machine is formed as a hydraulic pump and, for example, discharges to the first working line via the first power transmission unit and to the second working line via the second power transmission unit. . Therefore, the hydraulic piston machine of the present invention can also be applied to fluid circuits supplied independently of each other.

  According to claim 2 of the present invention, the two power transmission groups of the hydraulic piston machine are adjusted independently. As a result, when a hydraulic piston machine is used as the hydraulic pump, first, the discharge capacity can be adjusted via the first power transmission group. Next, similarly, for example, adjustment in the same direction is performed via the second power transmission group. It is particularly advantageous that separate discharge rates are set when discharging into two fluid circuits. In this case, by adjusting the two power transmission groups independently of each other, one power transmission group can be executed with a constant stroke volume, and on the other hand, the second power transmission group can also be executed and can be adjusted. become. Specifically, the first power transmission group is formed of a first piston group and a cylinder recess that are disposed in a cylinder recess of the cylinder drum unit. The second power transmission group is formed by the second cylinder recess of the second cylinder drum unit and the second piston group. Adjustment is performed by changing the rotation axis of each cylinder drum unit. Specifically, the rotation axis of each cylinder drum unit changes independently of the direction of the rotation axis of the other cylinder drum unit. Although the rotation axes of the cylinder drum units can be changed independently of each other, depending on the application, the rotation axes of the two cylinder drum units can be adjusted together.

  A preferred development of the hydraulic piston machine according to the invention is indicated in the dependent claims.

  A particularly preferred embodiment is to provide a swash plate that can be adjusted in two opposite directions from the neutral position in order to individually adjust the swing angle of the cylinder drum unit. As a result, when discharging to at least two different fluid circuits, the discharge direction can be reversed in the two fluid circuits. The reversal of the ejection direction may be performed independently of each other. In this regard, the neutral position need not coincide with the traveling sliding surface of the swash plate that is perpendicular to the drive shaft. A small angle that compensates for hydraulic pressure loss between the swash plate orientation and the drive shaft orientation also defines the neutral position.

  It is also preferable to set the swash plate by an adjusting device that performs linear motion. The entire unit is obtained in an elongated configuration by an actuating device that performs linear motion. In particular, such a linear motion can be easily obtained by the hydraulic load adjustment piston. This is particularly suitable for the point of linear movement parallel to the drive shaft. By performing linear motion in parallel with the drive shaft in this way, the adjustment device can be arranged in parallel with the drive shaft.

  The supply and removal of the pressure medium to and from the first and second cylinder chambers is preferably performed via a swash plate. For this reason, the pressure medium flow path is provided in the swash plate. The pressure medium flow paths of the first and second swash plates preferably communicate with the flow path portions of the first and second housing flange portions, respectively. Further, this arrangement suitably releases the hydraulic pressure of the swash plate. For this reason, the leakage fluid that leaks when passing from the pressure medium flow path of the swash plate to the flow path portions of the first and second housing flange portions is caused by each swash plate and the corresponding first bearing surface of the first housing flange portion. And a hydrostatic layer between the corresponding second bearing surfaces of the second housing flange. Therefore, the first and second swash plates are respectively slidably disposed on the first housing flange portion and the second housing flange portion, respectively, and release the hydraulic pressure by a small amount of leakage of the pressure medium. Therefore, it is not necessary to supply a special pressure medium to lubricate the swash plate.

  At least one operation connection that can be connected to the first and second cylinder chambers is formed in each of the first housing flange portion and the second housing flange portion via the pressure medium flow paths in the first and second swash plates. The The connection thus leads to the outside by a short path in the hydraulic piston machine. Each actuating connection is connected to a supply valve unit, whereby not only the pressure medium is post-supplied, but also has a high-pressure limiting valve that protects the connected working line.

  It is also preferred to provide a common supply pressure flow path for the first housing flange portion, the further housing portion, and the second housing flange portion. The pressure medium discharged later through this common supply pressure channel is supplied to the supply valve unit. The common supply pressure flow path is preferably, for example, a central connection that is sufficient to post-discharge the pressure medium supplied by a fixed displacement pump. By using only one common connection, no additional junction points are required and the cost of installing the circuit in the hydraulic piston machine is reduced.

  BRIEF DESCRIPTION OF THE DRAWINGS Preferred embodiments of the hydraulic piston machine of the present invention are shown in detail on the basis of the drawings and the following description.

  A perspective view of the hydraulic piston machine 1 of the present invention is shown in FIG. The hydraulic piston machine 1 has a housing that includes a first housing flange portion 2 and a second housing flange portion 3. The first housing flange portion 2 and the second housing flange portion 3 are arranged on both sides of the substantially tubular housing portion 4 and are completed by forming a sealed housing. The drive shaft 5 is rotatably attached to the housing of the hydraulic piston machine 1. The first bearing 6 is disposed on the first housing flange portion 2 and the second bearing 7 is disposed on the second housing flange portion 3 in order to be rotatably attached to the drive shaft 5. The first bearing 6 and the second bearing 7 are preferably configured as rolling contact bearings.

  In order to connect the first housing flange part 2 and the second housing flange part 3 to the housing part 4, the individual parts of the housing are connected to each other by means of screws 8.

  The support plate 9 is firmly connected to the drive shaft 5 in a freely rotatable manner. The support plate 9 has a disc shape and is disposed in the approximate central region of the housing part 4. The first piston group 10 extends from the support plate 9 toward the first housing flange portion 2. The first piston group 10 is provided in common with the circumference of the support plate 9 although only one of the pistons is provided with a reference numeral for the sake of clarity. On the side away from the support plate 9, the pistons 9 engage with the cylinder recesses of the cylinders 11 arranged on the drum plate 14, respectively. The first drum plate 14, the first cylinder group 11, and the first piston group 10 form a first power transmission group.

  The second piston group 12 is disposed in the opposite direction to the opposing surface of the support plate 9, and similarly, the piston engages with the corresponding cylinder recess of the cylinder group 13 on the side away from the support plate 9, and the first piston group 11 pistons 11 are also arranged. FIG. 1 shows an opposing arrangement, where support plates 9 can be perforated. The second cylinder group 13 is disposed on the second drum plate 15. Therefore, the second power transmission group is formed on the opposite side of the support plate 9. The first cylinder group 11 is firmly fixed to the first drum plate 14 in the axial direction, and the second cylinder group 13 is firmly fixed to the second drum plate 15 in the axial direction, that is, to each of the drum plates 14 and 15. In contrast, lateral movement is possible. For this reason, the cylinders 11 and 13 are fixed in the axial direction (not shown). However, the cylinders 11 and 13 are slidable on the support surface of the first drum plate 14 and on the support surface 15 'of the second drum plate 15 shown in FIG. When the first drum plate 14 and the second drum plate 15 are inclined with respect to the drive shaft 5 during sliding, the piston 10 (not shown) on the first support surface of the first support plate 14 and the second The elliptical protrusion of the piston 12 on the second support surface 15 ′ of the support plate 15 is corrected.

  A spherical shape may be used instead of the support plane and the cylinder bottom. The corrective movement is linked to the tilting of the cylinders 11 and 13.

  In order to incline the first drum plate 14 or the second drum plate 15, the first drum plate 14 is supported by the first traveling sliding surface of the first swash plate 16, which cannot be confirmed in FIG. 1. The second support plate 15 is supported by the second traveling sliding surface 18 of the second swash plate 17. The angles of the first swash plate 16 and the second swash plate 17 with respect to the drive shaft 5 can be set independently of each other. Since the rotating shafts of the drum plates 14 and 15 are arranged with respect to the traveling sliding surface, all the cylinder drum units are fixed independently of each other via the swash plates 16 and 17 as a result. Since the first drum plate 14 and the second drum plate 15 are firmly and rotatably connected to the drive shaft 5, the first drum plate 14 side away from the first cylinder group 11 is the first swash plate 16 running sliding surface. To slide and rotate. The second drum plate 15 is firmly connected to the corresponding drive shaft 5 in a freely rotatable manner, and rotates on the traveling sliding surface 18 of the second swash plate 17.

  The piston 10 and the second piston group of the first piston group at the angles of the rotation axes of the first drum plate 14 and the second drum plate 15 set with respect to the drive shaft 5 by the first swash plate 19 and the second swash plate 17. The pistons 12 reciprocate in the first cylinder 11 and the second cylinder 13, respectively.

  The first swash plate 16 is configured as a rocker rocker so that the swing angle of the first swash plate 16 can be set, and the sliding surface 19 is separated from the traveling sliding surface (not shown) of the first swash plate 16. Formed on the other side. Further, the second swash plate 17 is configured as a rocking rocker, and the second sliding surface 20 is formed on the side of the second swash plate 17 away from the traveling sliding surface 18. The first sliding surface 19 and the second sliding surface 20 form rolling contact bearings with the bearing surfaces of the first housing flange portion 2 and the second housing flange portion 3, which will be described in detail below.

  The central hole is preferably elliptical and is provided in the drum plates 14 and 15 as a passage for the drive shaft 5 as well as in the swash plates 16 and 17 respectively.

  In order to connect the first cylinder chamber to the first fluid circuit, the first cylinder chamber is alternately connected to a high pressure connection and a low pressure connection. For this reason, an opening is provided in the cylinder bottom of the first cylinder 11 supported by the first drum plate 14, and similarly an opening is provided in the first drum plate 14 that supports each cylinder 11. These openings are connected to each other while the first drum plate 14 rotates together with the first cylinder 11 on the traveling sliding surface of the first swash plate 16, and are arranged on the traveling sliding surface of the first swash plate 16. Control the opening. The control opening is an opening of the pressure medium flow path formed in the first swash plate 16. Therefore, the pressure medium flow path connects the traveling sliding surface of the first swash plate 16 to the first sliding surface 19 of the first swash plate 16 facing in the opposite direction. The opening of the pressure medium flow path on the first sliding surface 19 side is formed so as to be connected to the low pressure connection or the high pressure connection of the first housing flange portion 2 regardless of the set swing angle of the first swash plate 16. Is done. In addition to the standard shaped control opening, notches or holes can be formed in the running sliding surface of the first swash plate to improve the reversing action, for example to reduce vibration.

  Correspondingly, two pressure medium flow paths are formed in the second swash plate 17, and a control opening is formed on the traveling sliding surface 18 side. Similarly, a corresponding opening is formed in the second flange portion 3, and the second sliding in which the pressure medium flow path faces in the opposite direction so as to form a permanent connection regardless of the set swing angle of the swash plate 17. Open to surface 20.

  As shown in FIG. 1, the adjusting device 21 cooperates with the second swash plate 17. The adjusting device 21 preferably moves linearly, which is shown with reference to FIG. The adjusting device 21 is disposed outside the housing part 4 so as to be substantially parallel to the drive shaft 5. The adjusting device 21 arranged in parallel cooperates with the second swash plate 17 via the sliding block and the operation lever 47 to adjust the inclination of the traveling sliding surface 18 with respect to the drive shaft 5 by linear motion. Adjustment can be made in both directions. For example, the normal line of the surface of the traveling sliding surface 18 coincides with the axis of the drive shaft 5 at the neutral position. The second swash plate 17 can be tilted in the positive angle direction and the negative angle direction from this neutral position. Therefore, the discharge direction of the second power transmission group can be reversed.

  The hydraulic piston machine of the present invention is intended for delivery to two separate fluid circuits. In this regard, the first cylinder drum unit having the first piston 10 is connected to the first fluid circuit via a first working line connection 22 and a second working line connection 23. The 1st action line connection 22 and the 2nd action line connection 23 are arranged in the 1st housing flange part 2, and the 1st action line channel 24 and the 2nd action are controlled by the control situation (Steuernieren) of the 1st swash plate 10. Each is transmitted to the working line via the pipe channel 25.

  Correspondingly, the control status of the second swash plate 17 is transmitted to the second fluid circuit via the third working line connection 26 and the fourth working line connection 28. Similarly, the second fluid circuit is formed as a closed circuit, and has a third working tube channel 27 and a fourth working tube channel 29 provided for supplying a pressure medium to the second housing flange portion 3. The third working pipe flow path 27 and the fourth working pipe flow path 29 are connected to each control state on the traveling sliding surface 18 of the second swash plate 17 and the third through the pressure medium flow path provided in the second swash plate 17. The working line connection 26 and the fourth working line connection 28 are connected.

  In order to individually adjust the first swash plate 16 and the second swash plate 17 that are inclined in two opposite directions from each neutral position, it is also possible to select discharge directions independent of each other in the first fluid circuit and the second fluid circuit. . Although not visible in FIG. 1, a further adjusting device is arranged on the back of the hydraulic piston machine 1 for adjusting the first swash plate 16. Similarly to the neutral position of the second swash plate 17, the neutral position of the first swash plate 16 coincides with the position where the traveling sliding surfaces of the first swash plate 16 and the second swash plate 17 are perpendicular to the drive shaft 5. There is no need. In particular, the neutral position of the first swash plate 16 may form an angle different from the neutral position of the second swash plate 17 with respect to the axis of the drive shaft 5.

  A common supply system is provided to post-discharge the pressure medium to the first fluid circuit and the second fluid circuit and protect the fluid circuit against high operating pressures. The first working tube flow path 24 is connected to a supply valve unit not shown in FIG. Further, the second working tube flow path 25 is connected to the second supply valve unit 30. The first working tube channel 24 and the second working tube channel 25 can be connected to the first connection channel 32 via the first supply valve unit and the second supply valve unit 30. A check valve that opens in the direction of the working line connections 22 and 23 is provided in each supply valve unit, and a high-pressure limiting valve is arranged in parallel with the check valve. When a very high pressure is operated in the closing direction of the check valve, the check valve can be avoided by the high-pressure limiting valve, so that the working pipe line corresponding to the direction of the first connection flow path 32 can be avoided. Release pressure.

  Correspondingly, the third working tube channel 27 and the fourth working tube channel 29 are connected to the second connection channel 33 via the third and fourth supply valve units 31, respectively. When a certain supply pressure fixed by the spring is exceeded, the first connection flow path 32 and the second connection flow path 33 are opened by the supply pressure limiting valve 34, whereby the first connection flow path 32 and the second connection flow path 33 are opened. Can release pressure to tank capacity. For example, when the tank capacity is the same as the internal capacity of the housing of the hydraulic piston machine 1, the pressure medium collected in the internal tank capacity of the hydraulic piston machine 1 is connected to the external tank capacity via a return pipe (not shown). Remove.

  The supply pressure generated by the auxiliary pump is supplied to the first connection flow path 32 and the second connection flow path 33 through the supply line connection 35 provided for the subsequent discharge of the pressure medium. For example, the auxiliary pump is a fixed displacement pump with a through drive arranged in the first or second housing flange portions 2 and 3. The corresponding housing flanges 2 and 3 have an intake connection so that the pressure medium can be removed from the tank volume. The connection flow paths 32 and 33 are formed so as to overlap the housing portion 4, the first housing flange portion 2, and the second housing flange portion 3. The supply line connection 35 and the supply pressure limiting valve 34 are arranged in the housing part 4 and have a pressure limiting function in the supply system for the supply valve unit of the first housing flange part 2 and the supply valve unit of the second housing flange part 3. Dominate all together.

  If the pressure in the working line is a low pressure lower than the supply pressure, the pressure medium is post-supplied to the low pressure side via the supply valve units 30, 31 corresponding to the working line channels 24, 25, 27 and 29, respectively. The

  A partial cross-sectional view of the hydraulic piston machine of the present invention shown in FIG. 1 is shown in FIG. It can be seen that a first stopper 37 and a second stopper 38 are formed on the guide rod 36 in a portion passing through the adjusting device 21. The first spring hanger 39 and the second spring hanger 40 are arranged to slide on the guide rod 36 between the first stopper 37 and the second stopper 38. The compression spring 41 is formed as a spiral spring in this embodiment, but is disposed between the first spring hanger 39 and the second spring hanger 40. The outer circumferences of the first spring hanger 39 and the second spring hanger 40 are movably disposed in the recess of the adjustment piston 42.

  The deflection of the adjustment piston 42 to the right is shown in FIG. The drive element is provided in the recess of the adjustment piston 42 and supports the first spring hanger 39, so that the adjustment piston 42 moves to the right. The compression spring 31 supports and compresses the second spring hanger 38 with the second stopper 38 of the guide rod 36. When moving in the opposite direction, the spring 41 is supported by the first spring hanger 39 on the adjustment piston 42 until the first spring hanger 39 contacts the stopper 37. Further, when the adjustment piston 42 moves to the left side, the second spring fixing device 40 moves the drive element of the adjustment piston 42 to the left side, which is not shown in FIG. 2, and the first stopper 37 and the second of the adjustment piston 42. The spring 41 is compressed by contact with the drive element.

  The first working pressure chamber 43 and the second working pressure chamber 44 are provided for the adjustment piston 42 to bend from a stationary position defined by the spring 41. The working pressure chambers 43 and 44 are formed between the outer periphery of the adjusting piston 42 and the housing part 4 ′ of the adjusting device 21 formed by the housing part 4. In order to generate an axial hydraulic pressure in the adjusting piston 40, a surface that can be loaded with the operating pressure by separating the two operating pressure chambers 43 and 44 from each other by forming a radially enlarged region in the adjusting piston 42. Is formed in each of the working pressure chambers 43 and 44. A sliding block 46 cooperating with the operating lever 47 is formed at the end of the adjusting piston 42 away from the guide rod 36. The operation lever 47 is firmly connected to the second swash plate 17, and the linear motion of the sliding block 46 causes the second swash plate 17 to rotate. In order to change the working pressure of the working pressure chambers 43 and 44 that act oppositely, for example, a pilot valve is used as is known per se and is connected to the first working pressure chamber 43 and the second working pressure chamber 44 ( Not shown).

  An external view of the hydraulic piston machine 1 of the present invention is shown in FIG. The adjusting device 21 is arranged in the region of the housing part 4. Here, the guide rod 36 protrudes from a cover portion 48 that is preferably disposed on the first housing flange portion 2. Since the guide rod 36 is preferably fixed through the cover portion 48, the axial position of the guide rod 36, and hence the neutral position of the second swash plate 17, can be set by the rotation of the guide rod 36. A lock nut 49 fixes the shaft position.

  A partial cross section of the hydraulic piston machine of the present invention is shown in FIG. Here, the housing part 4 ′ of the adjusting device 21 is formed in the housing part 4 closed on both sides by the first housing flange part 2 and the second housing flange part 3. The housing part 4 ′ is closed on one side by the first cover part 48 and closed on the other side by the second cover part 50 of the second housing flange part 3. The second cover part 50 accommodates the sliding block 46 area and the operating lever 47 area.

  FIG. 5 further shows two supply valve units 51 and 52 in addition to the supply valve units 30 and 31 already shown in FIGS. Further, an adjusting device 53 is provided corresponding to the arrangement of the adjusting device 21 of the second swash plate 17, which cooperates with the first swash plate 16 and is located on the housing portion 4 on the opposite side of the housing portion 4 ′. Placed in the section. Furthermore, the structure of the adjusting device 53 of the first swash plate 16 corresponds to the adjusting device 21 described above. A cover portion 55 is provided in the first housing flange portion 2 to accommodate the sliding block of the adjusting device 53. The 1st connection flow path 32 consists of the 1st part 32a and the 2nd part 32b which are formed in the housing part 4 and the 1st housing flange part 2, respectively. Correspondingly, the second connection flow path 33 includes a first portion 33 a formed in the housing portion 4 and a second portion 33 b formed in the second housing flange portion 3. In order to post-discharge the pressure medium to the first working tube flow channel 24 and the second working tube flow channel 25, the second portion 32b of the first connection flow channel 32 includes the first flow channel portion 32 ′ and the second flow channel. Branch to the road portion 32 ″.

  The corresponding second portion 33b of the second connection channel 33 branches into a third channel part 33 'and a fourth channel part 33 ".

  Here, the branches of the first connection flow path 32 and the second connection flow path 33 are formed in the first housing flange portion 2 and the second housing flange portion 3, respectively. This means that only one flow path opening needs to be closed each time it passes from the housing part 4 to the first housing flange part 2 or the second housing flange part 3.

  The first housing flange portion 2 is shown in FIG. Bearing surfaces 60 ′ and 60 ″ are formed in the first housing flange portion 2, and the surface thereof corresponds to the curvature of the first sliding surface of the first swash plate 16. The first working tube flow path 24 and the second working tube. The flow path 25 opens to the first opening 24 ′ and the second opening 25 ′ at the bearing surfaces 60 ′ and 60 ″, respectively. In this case, the size of the first opening 24 'and the second opening 25' is preferably the same as the hydraulic piston machine 1 with reversible control. The first opening 24 ′ and the second opening 25 ′ preferably extend along the bearing surfaces 60 ′ and 60 ″. From the opening of the pressure medium flow path of the first swash plate 16 on the sliding surface 19. Leakage fluid generated when passing through the first working tube channel 24 and the second working tube channel 25 forms a lubricating film on the bearing surfaces 60 and 60 '. The resulting first swash plate 16 is smoothed by a lubricating film on the bearing surfaces 60 'and 60 ". Recesses 62a, 62b and 62c are formed adjacent to the bearing surface to contain leakage fluid and release hydraulic pressure. The recesses 62a, 62b and 62c are sealed with side walls with respect to the swash plate 16.

  FIG. 7 is a perspective view showing the first housing flange portion 1 slightly modified. The form of the second housing flange portion 3 corresponds to the first housing flange portion 2.

  FIG. 8 shows the first housing flange 2 upside down. A cover portion 55 is formed on the first housing flange portion 2 and includes a recess 61 for receiving the operating lever 47 and the sliding block 46 of the adjustment piston 42.

  FIG. 9 further shows the first flange portion 2.

  The invention is not limited to the described embodiments. The features shown in the embodiments can be combined with one another in a desired manner.

FIG. 1 is a first perspective view of a hydraulic piston machine of the present invention. FIG. 2 is a second perspective view including a partial cross-sectional view in the adjusting device of the hydraulic piston machine of the present invention. FIG. 3 is an external view of the hydraulic piston machine of the present invention. FIG. 4 is a second external view including a partial cross-sectional view in the adjusting device of the hydraulic piston machine of the present invention. FIG. 5 is a further perspective view of the hydraulic piston machine of the present invention. FIG. 6 is a first schematic perspective view of the first housing flange portion. FIG. 7 is a second schematic view of the first housing flange portion. FIG. 8 is a third schematic view of the first housing flange portion of the hydraulic piston machine of the present invention. FIG. 9 is a fourth schematic view of the hydraulic piston machine of the present invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Hydraulic piston machine 2 1st housing flange part 3 2nd housing flange part 4 Housing part 5 Drive shaft 6 1st drive bearing 7 2nd drive bearing 10 1st piston group 11,14 1st cylinder drum unit 12 2nd piston group 13, 15 Second cylinder drum unit 16 First swash plate 17 Second swash plate 21, 53 Adjusting device 22, 23, 26, 28 Working pipe connection 24, 25, 27, 29 Working pipe flow path 30, 51, 31, 52 Supply valve unit 32a, 32b, 33a, 33b Common supply pressure channel 60 ', 60 "First bearing surface

Claims (14)

A first swash plate (16) that supports a first cylinder drum unit (11, 14) in which a first piston group (10) is disposed in a cylinder recess of the first cylinder drum unit (11, 14), and a second cylinder drum unit ( The second swash plate (17) supports the second cylinder drum unit (12, 15) in which the second piston group (12) is disposed in the cylinder recess of the cylinder (12, 15).
The first piston group (10) and the second piston group (12) are rotatably and firmly connected to the drive shaft (5) of the hydraulic piston machine, and the cylinder recess of the first cylinder drum unit (11, 14). And the first piston group (10) are connectable to the first fluid circuit, and the cylinder recess of the second cylinder drum unit (12, 15) and the second piston group (12) A hydraulic piston machine, characterized in that the second cylinder chamber formed in (1) can be connected to a second fluid circuit. A first swash plate (16) that supports a first cylinder drum unit (11, 14) in which a first piston group (10) is disposed in a cylinder recess of the first cylinder drum unit (11, 14), and a second cylinder drum unit ( The second swash plate (17) supports the second cylinder drum unit (12, 15) in which the second piston group (12) is disposed in the cylinder recess of the cylinder (12, 15).
The first piston group (10) and the second piston group (12) are rotatably and firmly connected to the drive shaft (5) of the hydraulic piston machine, and the first piston unit (11, 14) of the first cylinder drum unit (11, 14). Hydraulic piston machine, characterized in that the rotary shaft and / or the second rotary shaft of the second cylinder drum unit (12, 15) can be adjusted independently of each other.   The swash plate (16, 17) can be adjusted in two opposite directions from the neutral position, and the first rotating shaft of the first cylinder drum unit (11, 14) and / or the second cylinder drum unit (12, 15). The hydraulic piston machine according to claim 1, wherein the hydraulic piston machine is provided for adjusting the second rotating shaft.   4. The hydraulic piston machine according to claim 1, wherein each swash plate (16, 17) cooperates with an adjusting device (21, 53) for linear movement. 5.   The hydraulic piston machine according to claim 4, wherein the linear motion can be performed in parallel with the drive shaft (5).   The first cylinder chamber defined by the first cylinder drum unit (11, 14) and the first piston group (10), and the second cylinder drum unit (12, 15) and the second piston group (12). 18. Any of the preceding claims, wherein a pressure medium flow path is disposed in each of the first and second swash plates (16, 17) to connect the second cylinder chamber to be connected to one or more fluid circuits. The hydraulic piston machine described.   At least one of the pressure medium flow paths of the first and second swash plates (16, 17) is connected to each working pipe flow path (24, 25, 27, 29) of the first and second housing flange portions (2, 3). The hydraulic piston machine according to claim 6, which opens to the bottom.   A first swash plate (16) is attached to the first housing flange (2) to release hydraulic pressure, and a second swash plate (17) applies hydraulic pressure to the second housing flange (3). 8. A hydraulic piston machine according to any of claims 6 and 7, which is mounted for release.   The first swash plate (16) is attached to slide on the first bearing surface (60 ′, 60 ″) of the corresponding first housing flange portion (2), and the second swash plate (17) The hydraulic piston machine according to claim 8, wherein the hydraulic piston machine is attached so as to slide on the second sliding surface of the second housing flange portion (3).   At least one of the working line connections (22, 23; 26, 28) is provided in the first housing flange part (2) and the second housing flange part (3), respectively, and each supply valve unit (30, 51; 31, The hydraulic piston machine according to any one of claims 6 to 9, wherein the hydraulic piston machine is connected to the working line connection of (52).   At least one of the working line connections (22, 23) of the first housing flange part (2) and at least one of the working line connections (26, 28) of the second housing flange part (3) are hydraulic piston machines The hydraulic piston machine according to claim 10, wherein the hydraulic piston machine is arranged toward one side.   The drive shaft (5) is mounted by at least a first drive bearing (6) of the first housing flange part (2) and a second drive bearing (7) of the second housing flange part (3). A hydraulic piston machine according to any one of the above.   The hydraulic piston machine (1) comprises a first housing flange part (2), a second housing flange part (3) and at least one further housing part to which the first and second housing flange parts (2, 3) are connected. The hydraulic piston machine according to any one of claims 1 to 12, comprising (4).   12. The common supply pressure channel (32a, b; 33a, b) is arranged in the first housing flange part (2), the second housing flange part (3) and at least one further housing part. Hydraulic piston machine.