HYDROSTATIC RADIAL PISTON UNIT

Abstract

Hydrostatic radial piston unit comprising a front case part accommodating a drive shaft via shaft bearing means so that the drive shaft can rotate around a central axis relative to the front case part. A rear case part is attached on one side to the front case part and closed on another side in order to define an internal volume. A cylinder block is disposed in the internal volume and attached to the drive shaft in a torque proof manner. Axially disposed timing holes in the cylinder block connect radially oriented working volumes in the cylinder block with a cylinder block front face that is arranged perpendicularly to the central axis and faces away from the front case part. Integrally within the rear case part internal annular flow passages are formed and are connected to an inlet and an outlet of the radial piston unit and running basically in circumferential direction around the central axis. Internal distribution conducts configured to hydraulically connect the internal annular flow passages with the cylinder block timing holes are integrally formed within the rear case part, too.

Claims

1. Hydrostatic radial piston unit (1) comprising: a front case part (10) accommodating a drive shaft (3) via shaft bearing means (16) so that the drive shaft (3) can rotate around a central axis (5) relative to the front case part (10); a rear case part (20) attached on one side to the front case part (10) and closed on another side in order to define an internal volume; a cylinder block (30) disposed in the internal volume and attached to the drive shaft (3) in a torque proof manner, wherein axially disposed timing holes (37) in the cylinder block (30) connect radially oriented working volumes (36) in the cylinder block (30) with a cylinder block front face (32) that is arranged perpendicularly to the central axis (5) and faces away from the front case part (10); wherein within the rear case part (20) internal annular flow passages (22) connected to an inlet (60) and an outlet (62) of the radial piston unit (1) and running basically in circumferential direction around the central axis (5), as well as internal distribution conducts (24) configured to hydraulically connect the internal annular flow passages (22) with the cylinder block timing holes (37), are formed integrally.

2. Hydrostatic radial piston unit (1) according to claim 1, further comprising a pressure force distribution plate (40) fixed to the rear case part (20) between the cylinder block (30) and the rear case part (20), comprising through holes (42) connecting the cylinder block timing holes (37) with the internal distribution conducts (24), wherein the through holes (42) are oriented parallel or inclined with respect to the central axis (5).

3. Hydrostatic radial piston unit (1) according to claim 1 or claim 2, further comprising a control bore (52) in the rear case part (20) to which the inlet (60), the outlet (62) and the internal annular flow passages (22) are connected, such that a control spool (54) movably accommodated in the control bore (52) is capable to guide hydraulic fluid from the inlet (60) to the internal annular flow passages (22) and to guide hydraulic fluid from the internal annular flow passages (22) to the outlet (62) via control recesses (55) arranged at the skin surface of the control spool (54).

4. Hydrostatic radial piston unit (1) according to claim 3, wherein in a full-torque position of the control spool (54) the timing holes (37) are in an alternating order connected to the inlet (60) or the outlet (62) via the internal distribution conducts (24), and wherein in a reduced-torque position of the control spool (54) less internal distribution conducts (24) are connected to the inlet (60) than in the full-torque position of the control spool (54).

5. Hydrostatic radial piston unit (1) according to claim 3 or 4, wherein the control spool (54) comprises at least one notch (56) which axially extends on the skin surface (57) from at least one of the control recesses (55) such that a fluid connection with reduced cross section can be established between the inlet (60) or outlet (62) and the internal annular flow passages (22).

6. Hydrostatic radial piston unit (1) according to claim 5, wherein the depth and/or width of the notch (56) in axial direction is constant or increases or decreases monotonically towards its dead end.

7. Hydrostatic radial piston unit (1) according to any of claims 3 to 6, wherein the diameter of the skin surface (57) of the control spool (54) is increased compared to control spools of prior art hydraulic radial piston units of comparable displacement volume and having a rear case part without internal annular flow passages integrally formed therein.

8. Hydrostatic radial piston unit (1) according to any of claims 3 to 7, wherein check valve means (58) are arranged inside the control spool (54), such that in the reduced torque-position hydraulic fluid can be provided to the internal annular flow passages (22), if the pressure in one of the internal annular flow passages (22) sinks below a predefined threshold.

9. Hydrostatic radial piston unit (1) according to any of the preceding claims, comprising a park brake mechanism (70) located on the rear side of the internal volume, wherein the brake discs (72) of the park brake mechanism (70) are arranged within the rear case part (20) and are disposed at least partially radially inside of the internal annular flow passages (22).

10. Hydrostatic radial piston unit (1) according to claim 9, wherein the park brake mechanism (70) is fail-safe and actuable hydraulically or electro-mechanically.

11. Hydrostatic radial piston unit (1) according to any of the preceding claims, wherein the rear case part (20) is closed by a housing cover (18) on the side facing away from the front case (10).

12. Hydrostatic radial piston unit (1) according to any of the preceding claims, wherein the working volumes (36) in the cylinder block (30) are sealed by radially moveable working pistons (34) arranged in working volumes (36), and wherein, under operational conditions of the radial piston unit (1), the piston movements are guided by cam lobes (13) on an inner cam surface (14) of a cam disk (12) against which the pistons (34) abut, wherein further the cylinder bores (36) and/or the pistons (34) comprising a surface-finished surface.

13. Hydrostatic radial piston unit (1) according to claim 12, wherein the number of working pistons (34) and the number of cam lobes (13) on the cam disk (12) is increased in comparison to prior art radial piston units of comparable displacement volume having a rear case part without internal annular flow passages integrally formed therein.

14. Hydrostatic radial piston unit (1) according to any of claim 12 or 13, wherein the cam disk (12) is integrally formed with the front case part (10).

15. Hydrostatic radial piston unit (1) according to any of the preceding claims, wherein one bearing means (16) is located in the rear case part (20) and another one is located in the front case part (10).

16. Hydrostatic radial piston unit (1) according to any of the preceding claims, wherein, under operational conditions of the radial piston unit (1), the opening forces exerted on the pressure force distribution plate (40) via the fluid pressure in the cylinder block timing holes (37) are balanced by pressure pistons (44) abutting against the pressure force distribution plate (40), and forced against the pressure force distribution plate (40) by means of pressure springs (48) and/or by fluid pressure.

17. Hydrostatic radial piston unit (1) according to claim 16, wherein the pressure pistons (44) are arranged coaxially in the internal distribution conducts (24).

18. Hydrostatic radial piston unit (1) according to any of the preceding claims, wherein the rear case part (20) is manufactured by sand casting, additive manufacturing technique or primary shaping technique with lost cores.

19. Hydrostatic radial piston unit (1) according to any of the preceding claims, wherein the cylinder block (30) comprises at least on one side an axial oriented recess (33) adjacent to an axial through bore (38), in which the drive shaft (3) is received, wherein the at least one recess (33) is provided for receiving part of a bearing inner or outer shell and/or at least partially the pressure force distribution plate (40).

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0028] The invention described above in general is now further detailed with the help of annexed figures, in which preferred embodiments and preferred design possibilities are shown; however, these preferred embodiments do not limit the scope of the inventive idea. Further modifications within the possibilities of the knowledge of a person with skills in the relevant art can be implemented without leaving the spirit of the invention. Furthermore, the shown preferred embodiments can be combined with one another without leaving the spirit of the invention. In the Figures it is shown:

[0029] FIG. 1 shows a longitudinal section cut of a radial piston unit according to the state of the art;

[0030] FIG. 2 shows a longitudinal section cut of a radial piston unit according to a first embodiment of the invention;

[0031] FIG. 3 shows a longitudinal section cut of a radial piston unit according to a second embodiment of the invention;

[0032] FIG. 4 shows a cross section through the radial piston unit according to FIG. 2;

[0033] FIG. 5 shows a control unit of the embodiment according to FIG. 2 in a detailed view.

DETAILED DESCRIPTION

[0034] In FIG. 1, a radial piston unit according to the state of the art is shown. Inside a front case part 10, a drive shaft 3 is mounted by means of bearing means 16, such that the drive shaft 3 can rotate around a central axis 5. The drive shaft 3 extents towards a rear case part 20, wherein on its free, protruding end a cylinder block 30 is fixed to the drive shaft 3 in a torque proofed manner. As can be seen in FIG. 1, drive shaft 3 is designed in a two-part manner, wherein the intersection/transition between the two parts of the drive shaft 3 is located in the area of cylinder block 30, such that both parts of drive shaft 3 can be driven by/can drive cylinder block 30. A person with relevant skills in the art knows that the second part of drive shaft 3 can be omitted if no park brake mechanism 70 is present at the radial piston unit, as the function of the second part of drive shaft 3 is basically to connect the cylinder block 30 with the park brake mechanism 70 mechanically. From FIG. 1, it can also be seen, that drive shaft 3independently if it is designed in a one- or two-part manneris supported only in the front case part 10 and protrudes towards the park brake mechanism 70 in the rear case part 20, where the drive shaft 3 is not supported.

[0035] The radial piston unit of FIG. 1 disposes, as seen in the longitudinal/axial direction, i.e. along the central axis 5 axially behind the cylinder block 30, radially inside the rear case part 20, a separate fluid distributor element 80. The fluid distributor element 80 shows a stepped cylindrical design, wherein at each step in radial direction an open circumferential groove is formed on the outside. The circumferential grooves on the fluid distributor element 80 form together with circumferentially running, radial inward open annular grooves in the rear case part 20 annular flow passages 82. The two annular passages 82 shown in FIG. 1 are at different pressure levels, which is indicated by different colors. The annular flow passages 82 are connected by means of distribution lines 84 formed within the fluid distributor element 80 to timing holes 37 located on the front face of cylinder block 30, which faces towards rear case part 20. In order to have the radial piston unit running, half the amount of the distribution lines 84 are charged with high pressure and the other half of distribution lines 84 guide low pressure to the outlet 62. In order that one half of the distribution lines 84 can be connected to one of annular passages 82 and the other half of the distribution lines 84 can be connected to the other annular flow passage 82, the annular flow passages 82 can be on different reference diameters. Therefore, the fluid distributor element 80 shows a stepped cylindrical design. Typically in the state of the art, eight or ten working volumes 36 are disposed within the cylinder block 30 for radial piston units showing a (total) volumetric size of 600 cc to about 950 cc, for instance.

[0036] In axial direction behind the rear case part 20, the radial piston unit 1 according to the state of the art shows a park brake mechanism 70, comprising a plurality of brake disc 72. As the functionality of such a park brake mechanism 70 is known to a person skilled in the art, further detailing is omitted.

[0037] In FIG. 2, a longitudinal section cut of a radial piston unit 1 according to the invention is shown, basically in the same orientation as the radial piston unit according to the state of the art shown with FIG. 1. Deviating from the state of the art, it can be seen from FIG. 2 that no separate fluid distributor element 80 is present. According to the invention, the functions of the distributor element 80 of the state of the art are integrated in the rear case part 20. Especially, internal annular flow passages 22 are formed integrally within the rear case part 20 as well as internal distribution conducts 24, which connect the internal annular flow passages 22 with the timing holes 37 located at the front face 32 of the cylinder block 30. As the internal distribution conducts 24 as well as the internal annular flow passage 22 are designed to be cavities in the rear case part 20, each of the internal distribution conducts 24 can be designed individually with a greater freedom in design, as neither a machining of these annular flow passages 22 and internal distribution conducts 24 nor a machining of a fluid distribution part is necessary.

[0038] Due to the greater freedom in design for arranging the internal annular flow passages 22 and the internal distribution conducts 24, these elements can be packed closer to each other and/or can be moved towards the radial outside of the rear case part 20. As a consequence, more internal space is available radial inwards of rear case 20. This bigger internal volume in the rear case part 20 can be used, according to the invention, for other elements part of a radial piston unit 1, e.g., in order to reduce the total axial length of radial piston unit 1.

[0039] In FIG. 2, a plurality of possibilities to reduce the total axial length of a radial piston unit 1 according to invention are shown, which can be implemented separately but also together corresponding to the requirements/functions which have to be fulfilled by the radial piston unit 1.

[0040] In one exemplary embodiment, the brake discs 72 of a park brake mechanism 70 are placed inside the rear case part 20, i.e. radially inside the internal annular flow passages 22 and the internal distribution conducts 24, respectively. In the prior art, at this location the fluid distributor element 80 was arranged.

[0041] In an another preferred embodiment shown with FIG. 2, a pressure force distribution plate 40 is located between the cylinder block 30 on that side of the cylinder block front face 32 on which the timing holes 37 are located, i.e. at that side of cylinder block 30 that faces towards the rear case part 20, and the rear case part 20. This pressure force distribution plate 40 is functioning, e.g., as running surface for the cylinder block 30. As the pressure force distribution plate 40 does not have to fulfill sealing functions to the rear case part 20 as the distribution element know from the art does, the pressure force distribution plate 40 can be designed specifically to fulfill its main functionality, i.e. to reduce friction for the turning cylinder block 30. For this, the pressure force distribution plate can be designed disc shaped as a basically standard shaped part of specific material reducing friction and wear at the cylinder block 30. As the pressure force distribution plate 40 is of simple geometry, one can also think about designing it as a wear part. As no other sealing requirements in radial direction have to be fulfilled by the pressure force distribution plate, like in the prior art by the fluid distributor element, the diameter of pressure force distribution plate 40 can be selected bigger in order to increase the running surface, which reduces friction forces and gives more axial stability to the cylinder block 30.

[0042] As shown with FIG. 2, the pressure force distribution plate 40 shows through holes 42 for connecting the internal distribution conducts 24 in the rear case part 20 with the timing holes 37 of cylinder block 30. Further, the pressure force distribution plate 40 is fixed in axial direction to the rear case part 20, for instance, in a kind of floating manner; simultaneously it is pressed by pressure force distribution pistons 44 (shown in FIG. 3) against the cylinder block front face 32, on which the timing holes 37 are arranged. When applying such a floating assembly manner, a hydrostatic bearing between the cylinder block front face 32 and the corresponding front face on the distribution plate 40 can be built up when the radial piston unit 1 according to the invention is operated. This is achieved by the fact that half of the through holes 42 through the pressure force distribution plate 40 are charged with high pressure in an alternating way with through holes 42 guiding expanded hydraulic fluid to the corresponding internal distribution conducts 24 in the rear case part 20, such that an opening/separating force at each second timing hole between the cylinder block 30 and the pressure force distribution plate 40 is created. In order to maintain the close contact between the cylinder block front face 32 and the pressure force distribution plate 40, distribution pistons 44 press the pressure force distribution plate 40 towards the cylinder block 30. As every second through hole in the pressure distribution plate 40 is charged with high pressure and the corresponding other through holes 42 are filled with at least hydraulic fluid under low pressure, a hydraulic fluid film can be established between the cylinder block front face 32 and the pressure force distribution plate 40. The pressure pistons 44 are mounted, for instance, in the rear case part 20 in blind holes 46 and pressed against the pressure distribution plate by means of springs 48. A person skilled in the art detects that this is only one of a plurality of possibilities to press the pressure distribution plate 40 against cylinder block 30. Thus, other possibilities, e.g., using a disc spring or charging the pressure pistons with hydraulic fluid under pressure, e.g., high pressure or case pressure, or any other possibility is covered by the inventive idea. A further possibility consist in arranging hollow pressure pistons 44 at the end of the internal distribution conducts 24, such that hydraulic fluid can pass through the pressure pistons 44 and, at the same time, pressure forces are generated at the ring surfaces facing to the internal distribution conducts 24, forcing the pressure pistons 44 against the pressure force distribution plate 40, and, furtheron, the pressure force distribution plate 40 against the cylinder block front face 32.

[0043] In implementation of the inventive idea, in another embodiment, the cylinder block 30 can be provided with a recess 33 on its side facing the front case part 10. In this recess 33, which is adjacent to the through bore 38 through which the drive shaft 3 passes, the inner shell of a bearing 16 can be accommodated at least partially, such that the total axial length of the front case part 10 and therewith the total axial length of the radial piston unit 1 can be reduced. This is also enabled by the inventive effect that the internal distribution conducts 24 can be arranged on a bigger reference diameter than it is possible with the state of the art design. Hence, the working volumes 36 can be arranged to the radial outside freeing space for the recesses 33.

[0044] With moving the working volumes 36 to the radial outer region, their diameter, i.e. the diameter and the height of the working pistons 34, can be reduced without reducing available torque. By reducing the working volumes 36 in diameter, an increased amount of working volumes 36 around the circumference can be arranged, e.g. 12 working volumes 36. So, the total volumetric size compared to radial piston unit of the prior art with comparable radial outer dimensions can be maintained or even increased. Thus, the available torque can be maintained or even increased with respect of radial piston units known from the prior art.

[0045] In another embodiment as shown in FIG. 3 of the invention, one of the two bearings 16, which are used in the state of the art at the front case part 10 area to support drive shaft 5 in a protruding manner, can be moved according to the invention to the rear case part 20 area. This can be done because no separate fluid distributor part 80 is present any longer in the rear case part 20 area. In the radial piston units of the state of the art, such a bearing 16 in the area of the rear case part 20 could not have been implemented in order not to endanger the sealing conditions between the separate fluid distributor part 80 and the rear case part 20. According to the invention, as the distribution system is integrally formed within the rear case part 20, one of the two bearings 16usually a roller or a needle bearingcan be moved to the rear case part 20 region. This reduces substantially the axial length of front case part 10 without enlarging the axial length of rear case part 20. A person skilled in the art obviously derives from FIG. 3 also that when a bearing 16 is arranged at the rear case part 20, and when no park brake mechanism 70 is needed, a very compact radial piston unit design with a minimum axial length is achieved. However, as depicted with FIG. 3, both assembly groups, i.e. the bearing means 16 as well as the park brake mechanism 70, can at least partially be integrated radially inside of rear case part 20. Thereby, the axial length compared to a radial piston unit according to the state of the art is reduced significantly.

[0046] In a further embodiment shown as well in FIG. 3, a control unit 50 can be integrated into the rear case part 20, as well. Such a control unit 50 comprises a control bore 52, within which a control spool 54 is movably disposed in axial direction of the control bore 52. Control spool 54 comprises one or more control recesses 55 for opening and closing an inlet 60 and an outlet 62 of a radial piston unit 1, respectively. Such control units 50 are well known in the state of the art, hence, explanation to its functionality can be omitted. However, the control unit 50 according to the present invention deviates from commonly known control units in that the diameter of the control bore 52 as well as the corresponding diameter of the control spool 54 can be chosen bigger than it is possible with integrated control units 50 in rear cases of radial piston units known from the art, having comparable radial outer dimensions. This especially applies to radial piston units with a comparable volumetric size. For example for radial piston units of the volumetric range between 600 cc and 950 cc in the state of the art control spools with a diameter of about 18 mm were used. In radial piston units according to the invention control spool diameters of about 30 mm or more are possible. Obviously, in bigger rear cases of bigger volumetric radial piston units bigger control units can be implemented. However, when comparing rear cases according to the invention to ones according to the state of the art having more or less the same radial outer dimensions, the inventive idea to integrate the internal flow passages 22 and the internal distribution conduct 24 into the rear case part 20 provides more space for the control unit 50. Hence, a bigger control spool diameter can utilized.

[0047] When utilizing such a control spool 54 increased in diameter, a better control of the radial piston unit 1 is possible, as, known to a skilled person, bigger control surfaces or control ring surfaces or bigger differences of two control surfaces or control ring surfaces are realizable. Further, bigger control surfaces provide greater control forces and, therefore, more accuracy in positioning the control spool with lower hysteresis and with a higher displacement speed.

[0048] With increasing the diameter of control spool 54, a smoothening notch 56 extending axially from at least one recess 55 at control spool 54 in axial direction, having a dead end, can be redesigned and optimized for fulfilling a better functionality. Such smoothening notches 56 are known from the state of the art, too, and are introduced to control spools 54 in order to smoothen operating condition changes, for instance, switching from a full torque operating condition of the radial piston unit to half torque/double speed operating condition. This especially is important when the used hydraulic fluid is still cold and shows a high viscosity. Here, it is obvious for a person skilled in the art that the cross section of such a smoothening notch 56 has great influence when changing from one operational state to another. By applying the inventive idea to radial piston units, these smoothing notches 56 can be designed as constant or continuously reducing grooves with possibly bigger cross sections reducing towards the dead end of a smoothing notch 56. In the state of the art, these notches show a stepped design.

[0049] In a further embodiment of the radial piston unit according to the invention, it is also possible to move the internal distribution conducts 24 radially outwards of the internal annular flow passages 22, i.e. to move the internal annular flow passages 22 radially inside of the internal distribution conducts 24. By doing this, the timing holes 37 in the cylinder block 30 can also be moved towards the radial outside of the cylinder block 30. Thereby, if necessary, reducing the working volumes 36 in the cylinder block 30. In order to not lose volumetric size of the radial piston unit, the number of working spaces 36, i.e. the number of cylinders and working pistons 36 can be raised, as the working volumes 36 can be arranged on a greater reference diameter. So, for instance for 600 cc to 950 cc radial piston units, it is possible to increase the number of working pistons 34 to twelve. For this exemplary range of volumetric sizes the number of working volumes was limited up to now in the state of the art to a number of ten by using a cam disc with six cam lobes, for instance. By increasing, according to the invention, the number of working pistons 34 to twelve for radial piston units with comparable volumetric size, and using a cam disc 12 having nine cam lobes 13, a 3-speed radial piston unit can be realized, for example.

[0050] As known from the art, when some working volumes will not be charged with high pressure, i.e. no high pressure is supplied to part of the timing holes, the torque of the radial piston unit drops, however, its speed increases. Here, it has to be guaranteed that a sufficient number of working volumes is charged with high pressure. Other non-pressurized working volumes are usually short-circuited and do not discharge hydraulic fluid to the outlet, for instance. When utilizing a cylinder block having twelve working volumes, operating states with charging only eight or only four of the twelve working volumes with high pressure is imaginable. Finally, by applying the inventive idea to a radial piston unit, three operating conditions having full torque, two thirds of full torque or only one third of full torque, is possible. Correspondingly, for fulfilling the performance equation of volumetric size multiplied by rotational speed, the rotational speed increases reciprocally with reducing working volumes charged with high pressure.

[0051] In a further embodiment according to the invention, as the control spool 54 of the integrated control unit 50 is increased in diameter with respect to a comparable situation in the state of the art, inside the control spool 54, check valve means 58also called anti-cavitation meanscan be introduced to guarantee that a minimum pressure is maintained in the internal annular flow passages 22, i.e. in at least the ones which are short-circuited working volumes 36 when the radial piston unit is operated in a reduced torque condition.

[0052] From the above disclosure and the accompanying Figures and claims, it will be appreciated that the hydraulic radial piston unit 1 according to the invention offers many possibilities and advantages over the prior art. All modifications and changes within the scope of the claims are intended to be covered thereby. It should be further understood that the examples and embodiments described above are for illustrative purposes only and that various modifications, changes or combinations of embodiments in the light thereof, which will be suggested to a person skilled in the relevant art, are included in the spirit and purview of this application.