Fluid devices

Abstract

To provide a fluid device capable of downsizing and saving a space with a simple structure.SOLUTION: A fluid device 1 has a first housing 45 that has first channels 111 to 114, second housings 2, 3, and 35 that have second channels 41 and 42 the number of which is more than that of the first channels, and a distribution plate 100 that is sandwiched in a thickness direction while end surfaces 101 and 102 are respectively contacted with the first housing and the second housing, and has third channels 103 to 107 connecting predetermined first channel and second channel. The third channel has a plurality of penetration channels 103 aligned in a circumferential direction and opening to the end surface, and coupling groove channels 104 and 105 formed in the circumferential direction along the end surface and coupling the plurality of penetration channels.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] The present invention relates to fluidic devices. [Background technology]

[0002] A known hydraulic pump-motor is described in Patent Document 1. This document describes an oil passage for circulating hydraulic oil at different positions circumferentially relative to a main shaft. Patent Document 1 also describes a restraining member 130 as a configuration for forming an oil passage for supplying hydraulic oil. The restraining member 130 has a groove formed in a concave shape on its outer circumferential surface and a through-hole formed radially inward of the groove and penetrating in the axial direction. These grooves and the axial through-hole are selectively connected to each other. Furthermore, the document describes that the restraining member 130 is shrink-fitted into a cylindrical recess 186 that surrounds the entire radial outer circumference of the restraining member 130. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Japanese Patent Application Laid-Open No. 2002-202069 Summary of the Invention [Problem to be solved by the invention]

[0004] However, in the configuration of Patent Document 1, the oil passage is formed between the outer peripheral surface of the restraint member 130 and the inner peripheral surface of the cylindrical recess 186, resulting in multiple recessed grooves being formed in the axial direction on the outer peripheral surface of the restraint member 130. For this reason, the axial dimension of the restraint member 130 cannot be reduced structurally in order to supply and discharge hydraulic oil to drive the fluid device. In other words, there was a problem in that the fluid device could not be made thinner.

[0005] The present invention provides a fluid device that has a simple structure and can be made smaller and requires less space. [Means for solving the problem]

[0006] A fluidic device according to one aspect of the present invention comprises: a first housing having a first flow path; a second housing having more second flow paths than the first flow paths; a distribution plate that is sandwiched in a thickness direction with end surfaces thereof in contact with the first housing and the second housing, and has a third flow path that connects a predetermined one of the first flow paths and the second flow path; and The third flow path is a plurality of through-flow passages arranged side by side in a circumferential direction and opening on the end surface; a connecting groove flow path formed in a circumferential direction along the end surface and connecting the plurality of through-flow paths; The above problem has been solved by providing the above.

[0007] According to one aspect of the fluid device of the present invention, a distribution plate having a connecting groove formed on an end surface connects first and second flow paths, and fluid can be distributed to the second flow paths, which are larger than the first flow paths. This allows fluid to be distributed between the first and second flow paths in the direction from the first housing to the second housing solely by the thickness of the distribution plate. Therefore, compared to the conventional technology described in the aforementioned patent documents, it is possible to reduce the dimensions of the device configuration in the direction from the first housing to the second housing.

[0008] In the above configuration, the connecting groove flow passages can be formed on the end surfaces, which are the front and rear surfaces of the distribution plate.

[0009] In the above configuration, the plurality of through-flow passages aligned in the circumferential direction can be disposed at equal intervals on the end face.

[0010] In the above configuration, an outer circumferential connecting groove flow path is formed on the end surface along a circumferential direction and connects the plurality of through-flow paths radially outward of the plurality of through-flow paths; an inner circumferential connecting groove flow path formed in the end surface along a circumferential direction and connecting the plurality of through-flow paths radially inward of the plurality of through-flow paths; can have:

[0011] In the above configuration, an outer diameter direction groove flow path is formed on the end surface along a radial direction and connects the through flow path opening on the end surface and the outer periphery connecting groove flow path; an inner radial groove flow path formed in the end surface along a radial direction and connecting the through flow path opening at the end surface and the inner circumferential connecting groove flow path; and The outer radial groove flow passage and the inner radial groove flow passage may be respectively connected to the through-passages adjacent to each other in the circumferential direction, or the outer radial groove flow passage and the inner radial groove flow passage may be respectively connected to the through-passages adjacent to each other every other one in the circumferential direction.

[0012] In the above configuration, the arrangement of the outer radial grooves and the inner radial grooves can be repeated with two or four of the through-flow passages adjacent in the circumferential direction as one set.

[0013] In the above configuration, the inner connecting groove flow path, the plurality of through flow paths that are lined up circumferentially and open to the end face, and the outer connecting groove flow path can each be arranged on a concentric circle on the end face.

[0014] In the above configuration, the second housing is a swing housing portion having an axis; internal teeth provided on an inner peripheral surface of the swing housing portion; a carrier supported by the swing housing portion so as to be rotatable about the axis line via two bearings provided spaced apart from each other along the axis line of the swing housing portion; a crankshaft supported by the carrier so as to be rotatable about another axis parallel to the axis; an oscillating gear that is regulated to oscillating rotation by the crankshaft and meshes with the internal teeth; a supply / discharge plate having a plurality of supply / discharge flow paths that supply the working fluid between the inner peripheral surface of the oscillating housing portion and the oscillating gear and discharge the working fluid from between the inner peripheral surface of the oscillating housing portion and the oscillating gear; Equipped with The supply / discharge plate is disposed on the first housing side in a direction along the axis of the oscillating gear, and each of the supply / discharge flow paths can communicate with the second flow path.

[0015] In the above configuration, the inner circumferential connecting groove passage and the outer circumferential connecting groove passage formed on the end surface of the distribution plate can supply and discharge working fluids of different pressures or can supply and discharge working fluids of the same pressure.

[0016] According to another aspect of the present invention, a fluidic device includes: a first housing having a first flow path; a second housing having more second flow paths than the first flow paths; a distribution plate that is sandwiched in a thickness direction with end surfaces thereof in contact with the first housing and the second housing, and has a third flow path that connects a predetermined one of the first flow paths and the second flow path; and The second housing is a swing housing portion having an axis; internal teeth provided on an inner peripheral surface of the swing housing portion; a carrier supported by the swing housing portion so as to be rotatable about the axis line via two bearings provided spaced apart from each other along the axis line of the swing housing portion; a crankshaft supported by the carrier so as to be rotatable about another axis parallel to the axis; an oscillating gear that is regulated to oscillating rotation by the crankshaft and meshes with the internal teeth; a supply / discharge plate having a plurality of supply / discharge flow paths that supply the working fluid between the inner peripheral surface of the oscillating housing portion and the oscillating gear and discharge the working fluid from between the inner peripheral surface of the oscillating housing portion and the oscillating gear; Equipped with the supply / discharge plate is disposed on the first housing side in a direction along the axis of the oscillating gear, the supply / discharge flow paths communicate with the second flow path, and The third flow path in the distribution plate is a plurality of through-flow passages arranged side by side in a circumferential direction and opening on the end surface; a connecting groove flow path formed on each of the end faces, which are the front and rear surfaces of the distribution plate, and formed in a circumferential direction along the end faces to connect the plurality of through-flow passages; and a peripheral connecting groove flow path formed on the end faces along the circumferential direction to connect the plurality of through-flow passages radially outward of the plurality of through-flow passages; the connecting groove flow passage is an inner circumferential connecting groove flow passage formed in the end surface along a circumferential direction and connecting the plurality of through-flow passages radially inward of the plurality of through-flow passages; an outer radial groove formed on the end surface along a radial direction and connecting the through-flow passage and the outer circumferential connecting groove, the through-flow passage opening on the end surface; an inner radial groove flow path formed in the end surface along a radial direction and connecting the through flow path opening at the end surface and the inner circumferential connecting groove flow path; and The above problem was solved by having the outer radial groove passages and the inner radial groove passages connected to the through passages adjacent to each other in the circumferential direction, or by having the outer radial groove passages and the inner radial groove passages connected to the through passages that are adjacent to each other every other one in the circumferential direction, and by repeating the arrangement of the outer radial groove passages and the inner radial groove passages with four circumferentially adjacent through passages as one set.

[0017] With this configuration, the first flow path and the second flow path are connected by a distribution plate having connecting groove flow paths formed as grooves on the end surface, and the fluid can be divided and merged between the second flow paths and the first flow path, which are more numerous than the first flow paths. This makes it possible to distribute the fluid between the first flow path and the second flow path in the direction from the first housing to the second housing using only the thickness of the distribution plate. Therefore, it is possible to reduce the dimensions of the device configuration in the direction from the first housing to the second housing compared to the conventional technology described in the above-mentioned patent documents.

[0018] This eliminates the need to form multiple recessed grooves in the axial direction on the outer peripheral surface of the restraint member 130, as in the configuration of Patent Document 1. This allows the axial dimension to be reduced while still allowing the hydraulic oil to be supplied and discharged to drive the fluid device. In other words, the fluid device can be made thinner.

[0019] This improves sealing performance, eliminating the possibility of hydraulic oil leaking due to a gap occurring between the restraining member 130, which forms the flow path (oil passage), and the cylindrical recess 186, as in the configuration of Patent Document 1. Furthermore, by clamping and fastening the plate-shaped distribution plate between the first housing and the second housing, that is, by pressing it with a fastening member or the like, the deformation of the member due to the fastening or the like ensures a tight seal, thereby reliably improving sealing performance.

[0020] At the same time, since the distributor plate can be manufactured simply by forming a groove on the end face as the third flow path, it can be manufactured by cutting or casting, reducing the number of manufacturing steps and shortening the work time. Furthermore, since the required airtightness can be maintained simply by flattening the end face of the distributor plate, excessive machining precision is not required. This makes it possible to achieve both the required airtightness and ease of manufacturing. [Effects of the Invention]

[0021] According to the present invention, it is possible to provide a fluid device that has a simple structure, can be made smaller and more space-saving, can maintain the sealing of hydraulic oil, can prevent leakage of hydraulic oil, and can improve operating efficiency. [Brief explanation of the drawings]

[0022] [Figure 1] 1 is a partially cross-sectional side view of a hydraulic motor according to an embodiment of the present invention. [Figure 2] FIG. 2 is a cross-sectional view taken along line II-II in FIG. [Figure 3] FIG. 2 is an enlarged view of part III in FIG. [Figure 4]FIG. 2 is an enlarged view of a portion VI in FIG. [Figure 5] 2 is a cross-sectional view taken along line VV of FIG. 1, showing a flow path of the hydraulic motor according to the embodiment of the present invention. [Figure 6] 6 is a cross-sectional view taken along line VI-VI in FIG. 1, showing the flow paths of the distribution plate in the embodiment of the present invention. [Figure 7] 7 is a cross-sectional view taken along line VII-VII in FIG. 1, showing the flow paths of the distribution plate in the embodiment of the present invention. [Figure 8] FIG. 2 is a cross-sectional view showing a distribution plate according to an embodiment of the present invention. [Figure 9] 9 is a cross-sectional view taken along line IX-IX in FIG. 1, showing a flow path of the hydraulic motor according to the embodiment of the present invention. [Figure 10] 2 is a cross-sectional view taken along line XX in FIG. 1, showing a flow path of a hydraulic motor according to an embodiment of the present invention. [Figure 11] 1. FIG. 3 is a cross-sectional view taken along line XI-XI in FIG. 1, showing a flow path of the hydraulic motor according to the embodiment of the present invention. [Figure 12] 8 is a cross-sectional view corresponding to FIG. 7, illustrating another pressure state in the embodiment of the present invention. DETAILED DESCRIPTION OF THE INVENTION

[0023] A first embodiment of a fluid device according to the present invention will now be described with reference to the drawings. FIG. 1 is a side view, partially in cross section, showing a hydraulic motor as an example of a fluid device according to this embodiment. FIG. 2 is a cross-sectional view taken along line II-II in FIG. 1. FIG. 3 is an enlarged view of part III in FIG. 1. FIG. 4 is an enlarged view of part IV in FIG. 1. FIG. 5 is a cross-sectional view taken along line VV in FIG. 1. FIG. 6 is a cross-sectional view taken along line VI-VI in FIG. 1. FIG. 7 is a cross-sectional view taken along line VII-VII in FIG. 1. FIG. 8 is a cross-sectional view showing a distribution plate. FIG. 9 is a cross-sectional view taken along line IX-IX in FIG. 1. FIG. 10 is a cross-sectional view taken along line XX in FIG. 1. FIG. 11 is a cross-sectional view taken along line XI-XI in FIG. 1. In the figures, reference numeral 1 denotes a hydraulic motor.

[0024] The fluid device according to this embodiment will first be described as a hydraulic motor, but it can also be employed as a hydraulic pump.

[0025] <Hydraulic motor> As shown in Figures 1 to 4, the hydraulic motor 1 has a cylindrical oscillating housing portion 2 and a rotating portion 3 rotatably supported on the inner surface of the oscillating housing portion 2 via two bearings 12, 13 (first bearing 12 and second bearing 13). Angular contact ball bearings are used as the bearings 12 and 13. However, the present invention is not limited to this, and various bearings can be used, such as other ball bearings such as deep groove ball bearings and sliding bearings.

[0026] The central axis of the oscillating housing portion 2 coincides with the rotation axis of the rotating portion 3. In the following description, the central axis and the rotation axis are collectively referred to as a first axis C1 (an example of an axis). In addition, the direction parallel to the first axis C1 may be simply referred to as the axial direction, the rotation direction of the rotating portion 3 as the circumferential direction, and the radial direction of the rotating portion 3 as the radial direction.

[0027] <Swing housing part> The swing housing portion 2 is divided in the axial direction and comprises a first swing housing 7 arranged on a first axial direction side (left side in FIG. 1) and a second swing housing 8 arranged on a second axial direction side (right side in FIG. 1) opposite to the first axial direction. Note that the swing housing portion 2 may also be configured not to be divided in the axial direction. The first oscillating housing 7 is formed in a cylindrical shape. An outer flange portion 9 that protrudes radially outward is formed on the outer peripheral surface 7a of the first oscillating housing 7 near the first end portion 7b on the first direction side. The outer flange portion 9 is for attaching the hydraulic motor 1 to an external device (not shown). A through hole 9a for passing a bolt (not shown) is formed in the outer flange portion 9 in the thickness direction (axial direction) of the outer flange portion 9.

[0028] The peripheral wall 7e of the first oscillating housing 7 has a thick-walled portion 10 that is thicker than other portions, from a second end 7d on the second direction side to the center in the axial direction. A second end 10c on the second direction side of the thick-walled portion 10 is located on the same plane as the second end 7d of the first oscillating housing 7. In other words, the second end 10c of the thick-walled portion 10 forms part of the second end 7d of the first oscillating housing 7.

[0029] A plurality of pin grooves 10a (for example, 13 in this embodiment) are formed in the inner peripheral surface 10d of the thick-walled portion 10. Each pin groove 10a is formed in the entire thick-walled portion 10 along the axial direction and is arranged at equal intervals in the circumferential direction. The pin grooves 10a are formed in a semicircular shape when viewed in the axial direction. A cylindrical internal tooth pin (an example of an internal tooth) 90 is rotatably housed in each pin groove 10a. Because the pin grooves 10a are formed in a semicircular shape when viewed in the axial direction, the internal tooth pin 90 protrudes radially inward by a semicircular amount from the inner peripheral surface 10d of the thick-walled portion 10. The internal tooth pin 90 functions as an internal tooth that meshes with the oscillating gear 5, which will be described later.

[0030] First through holes 19 are formed in the outer periphery of the thick-walled portion 10 between the pin grooves 10a, penetrating the thick-walled portion 10 in the axial direction. The first through holes 19 are arranged at equal intervals in the circumferential direction. There are, for example, eight first through holes 19. Shanks 20a of bolts 20 (an example of a fixing portion and a screw) are inserted into these first through holes 19. The first oscillating housing 7, the second oscillating housing 8, and a supply / discharge plate 46 (described later) are fastened together and integrated by the bolts 20.

[0031] Furthermore, a first bearing accommodating portion 11 having a larger inner diameter is formed on the inner peripheral surface 7c of the first oscillating housing 7, closer to the first direction than the thick-walled portion 10, via a stepped portion 11a. An outer race 12a of a first bearing 12 is fitted into this first bearing accommodating portion 11. The first bearing 12 and the first oscillating housing 7 are positioned by the outer race 12a abutting against the stepped portion 11a.

[0032] A seal housing portion 14 having a larger inner diameter is formed on the inner peripheral surface 7c of the first oscillating housing 7, closer to the first direction than the first bearing housing portion 11, via a step portion 14a. A part of a seal portion 15 is fitted into this seal housing portion 14. The seal portion 15 provides a seal between the first oscillating housing 7 and the rotating portion 3. For example, a floating seal is used as the seal portion 15. However, the seal is not limited to this, and various seals such as a packing or a mechanical seal can be used.

[0033] A first carrier-side first labyrinth portion 16 is formed at the first end portion 7b of the first oscillating housing 7, with an inner diameter larger than that of the seal accommodating portion 14. The first carrier-side first labyrinth portion 16 cooperates with the rotating portion 3 to form a first labyrinth 38. The first labyrinth 38 makes it difficult for dust and other foreign matter to enter between the first oscillating housing 7 and the rotating portion 3 from the outside.

[0034] The second end 7d of the first oscillating housing 7 corresponds to the dividing surface between the first oscillating housing 7 and the second oscillating housing 8 of the oscillating housing portion 2. The entire outer periphery of the second end 7d of the first oscillating housing 7 is formed flat. An annular O-ring groove 17 is formed in the second end 7d closer to the outer periphery than the first through-hole 19 when viewed from the axial direction. An O-ring 18 is fitted in the O-ring groove 17. The O-ring 18 ensures sealing between the first oscillating housing 7 and the second oscillating housing 8.

[0035] The second swing housing 8 is formed in an annular shape. A second through hole 22 communicating with the first through hole 19 is formed in the peripheral wall 8a of the second swing housing 8 at a position corresponding to the first through hole 19 of the first swing housing 7. The second through hole 22 is formed with the same diameter as the first through hole 19 and is positioned coaxially with the first through hole 19. A counterbore 23 is formed in most of the second direction side of the second through hole 22. The head 20b of the bolt 20 is inserted into the counterbore 23.

[0036] A first end 8b on the first direction side of the second oscillating housing 8 corresponds to the dividing surface between the oscillating housing portion 2 and the first oscillating housing 7. A presser plate 21 that protrudes radially inward from an inner peripheral surface 8c of the second oscillating housing 8 is integrally molded at the first end 8b of the second oscillating housing 8. The presser plate 21 is formed in an annular shape when viewed from the axial direction. The presser plate 21 closes, from the second direction side, working chambers 66a, 66b, 66c that are formed between the inner peripheral surface 7c of the first oscillating housing 7 and the outer peripheral surface of a oscillating gear 5 (described later). When the first swing housing 7 and the second swing housing 8 are integrated, the pressing plate 21 can be formed separately from the swing housing portion 2.

[0037] A second carrier-side first labyrinth portion 25 is formed on most of the inner peripheral surface 21a of the pressing plate 21, excluding the end portion on the first direction side. The second carrier-side first labyrinth portion 25 is formed by making the inner diameter larger than the inner diameter of the inner peripheral surface 21a of the pressing plate 21 via a step portion 25a. The second carrier-side first labyrinth portion 25 cooperates with the rotating portion 3 to form a second labyrinth 40. The second labyrinth 40 makes it less likely for hydraulic oil to leak between the second oscillating housing 8 and the rotating portion 3 (details will be described later).

[0038] A second bearing accommodating portion 24 having a larger inner diameter is formed on the inner peripheral surface 8c of the second oscillating housing 8, with a step portion 24a interposed between them, and is located closer to the second direction than the pressing plate 21. An outer race 13a of the second bearing 13 is fitted into this second bearing accommodating portion 24. The second bearing 13 and the second oscillating housing 8 are positioned when the outer race 13a abuts against the step portion 24a.

[0039] An O-ring groove 26 that is annular when viewed from the axial direction is formed on the outer periphery of a second end 8d on the second direction side of the second oscillating housing 8. An O-ring 27 is fitted in the O-ring groove 26. The O-ring 27 ensures sealing between the second oscillating housing 8 and a cover 29, which will be described later. A plurality of female thread portions 28 are formed at equal intervals in the circumferential direction at the second end portion 8d of the second oscillating housing 8, radially inward from the O-ring groove 26. These female thread portions 28 are used to fix a cover 29 to the second oscillating housing 8.

[0040] <Cover> The cover 29 closes the opening 8e of the second oscillating housing 8 from the second direction side. The cover 29 is formed, for example, by pressing a metal plate so that most of the center portion bulges out toward the second direction side. The outer periphery of the cover 29 is formed with an outer flange portion 29a. This outer flange portion 29a overlaps the second end portion 8d of the second oscillating housing 8.

[0041] The outer flange portion 29a has a through hole 29b formed therein that penetrates in the thickness direction at a position corresponding to the female thread portion 28 of the second oscillating housing 8. A bolt 30 is inserted into this through hole 29b from the second direction side, and the bolt 30 is tightened into the female thread portion 28 of the second oscillating housing 8, thereby fixing the cover 29 to the second oscillating housing 8.

[0042] <Supply / Discharge Plate> A supply / discharge plate (port plate) 46, which is fixed by bolts 20 inserted into the second through-holes 22 of the second oscillating housing 8 and the first through-holes 19 of the first oscillating housing 7, is disposed at a first end 10b on one side of the thick-walled portion 10. The supply / discharge plate 46 is a plate for supplying hydraulic oil (working fluid) to working chambers 66a, 66b, and 66c, which will be described later, and for discharging hydraulic oil from the working chambers 66a, 66b, and 66c.

[0043] The supply / discharge plate 46 is formed in an annular shape when viewed in the axial direction. The outer diameter of the supply / discharge plate 46 is approximately equal to or slightly smaller than the diameter of the inner circumferential surface 7c of the first oscillating housing 7. Therefore, the supply / discharge plate 46 is disposed at the first end 10b of the thick-walled portion 10 so as to fit into the inner circumferential surface 7c of the first oscillating housing 7.

[0044] A female thread portion 47 is formed on the outer periphery of the supply / discharge plate 46 at a position corresponding to the first through hole 19 of the first swing housing 7. A bolt 20 is inserted from the second swing housing 8 side into the second through hole 22 and then into the first through hole 19 of the first swing housing 7, and the bolt 20 is tightened into the female thread portion 47 of the supply / discharge plate 46. As a result, the first swing housing 7, the second swing housing 8, and the supply / discharge plate 46 are tightened together and integrated by the bolts 20.

[0045] The supply / discharge plate 46 has a plurality of through holes (supply / discharge ports) 46a formed therethrough in the thickness direction, radially inward of the female thread portion 47. Hydraulic oil is supplied to the working chambers 66a, 66b, and 66c via these through holes 46a, and hydraulic oil is discharged from the working chambers 66a, 66b, and 66c via these through holes 46a (details will be described later). The number of through holes (supply / discharge ports) 46a corresponds to the number of pin grooves 10a formed in the first oscillating housing 7. For example, in this embodiment, there are 13 through holes 46a. Each through hole (supply / discharge port) 46a is formed so that its opening on the thick-walled portion 10 side is located at the center between adjacent pin grooves 10a in the circumferential direction and radially inward of the inner circumferential surface 10d of the thick-walled portion 10.

[0046] A plate-side labyrinth portion 48 is formed on most of the inner circumferential surface 46b of the supply / discharge plate 46, excluding the end portion in the second direction. The plate-side labyrinth portion 48 is formed by making the inner diameter larger than the inner diameter of the inner circumferential surface 46b of the supply / discharge plate 46 via a step portion 48a. The plate-side labyrinth portion 48 cooperates with the rotating portion 3 to form a third labyrinth 49. The third labyrinth 49 makes it less likely for hydraulic oil to leak between the supply / discharge plate 46 and the rotating portion 3 (details will be described later).

[0047] <Rotating part> The rotating part 3, which is rotatably held in the oscillating housing part 2, mainly comprises a carrier part (rotating member) 6 rotatably supported on both axial sides via bearings 12, 13, a plurality of crankshafts 4 (for example, three in this embodiment) rotatably supported on the carrier part 6, and an oscillating gear 5 rotatably supported on the crankshafts 4. The carrier portion 6 is divided in the axial direction and is composed of a first carrier 31 arranged on the first direction side and a second carrier 32 arranged on the second direction side.

[0048] The first carrier 31 is integrally formed of a disk-shaped base plate portion 33 and a plurality of (for example, three in this embodiment) support pillar portions 34 that protrude in the second direction from the second end portion 33b on the second direction side of the base plate portion 33. The outer diameter of the outer peripheral surface 33c of the base plate portion 33 gradually increases from the second end portion 33b toward the first end portion 33a on the first direction side, via a step portion.

[0049] That is, the outer peripheral surface 33c of the base plate portion 33 has, in order from the second end portion 33b side, a first outer peripheral surface 33d, a second outer peripheral surface 33e having a larger outer diameter formed at the first direction side end of the first outer peripheral surface 33d via a large step portion 33h, a third outer peripheral surface 33f having a larger outer diameter formed at the first direction side end of the second outer peripheral surface 33e via a small step portion 33i, and a fourth outer peripheral surface 33g having a larger outer diameter formed at the first direction side end of the third outer peripheral surface 33f via a middle step portion 33j.

[0050] A portion of the first carrier 31 corresponding to the first outer peripheral surface 33d is inserted into the plate-side labyrinth portion 48 of the supply / discharge plate 46. The outer diameter of the first outer peripheral surface 33d is slightly smaller than the inner diameter of the plate-side labyrinth portion 48. The second end portion 33b of the first carrier 31 is located slightly in front of the stepped portion 48a of the supply / discharge plate 46. In this way, the first outer peripheral surface 33d of the first carrier 31, the second end portion 33b, and the plate-side labyrinth portion 48 of the supply / discharge plate 46 form a third labyrinth 49.

[0051] The inner race 12b of the first bearing 12 is fitted onto the third outer peripheral surface 33f. The first bearing 12 and the first carrier 31 are positioned by the inner race 12b abutting against the middle step portion 33j. This positions the first carrier 31 relative to the first oscillating housing 7. The first carrier 31 is rotatably supported relative to the first oscillating housing 7 via the first bearing 12.

[0052] The fourth outer peripheral surface 33g of the first carrier 31 faces the seal accommodating portion 14 of the first oscillating housing 7 in the radial direction. In other words, the seal portion 15 is disposed between the fourth outer peripheral surface 33g of the first carrier 31 and the seal accommodating portion 14 of the first oscillating housing 7.

[0053] A disk portion 35 having a circular shape when viewed from the axial direction is integrally formed with the first-direction side end of the fourth outer peripheral surface 33g. A second end portion 35b of the disk portion 35 on the second direction side faces the first end portion 7b of the first oscillating housing 7 in the axial direction. The outer diameter of the disk portion 35 is equal to the diameter of the outer peripheral surface 7a of the first oscillating housing 7. A seal accommodating recess 36 having an annular shape when viewed from the axial direction is formed on the outer periphery of the second end portion 35b of the disk portion 35. The seal accommodating recess 36 is smoothly connected to the fourth outer peripheral surface 33g. A portion of the seal portion 15 is also accommodated in the seal accommodating recess 36. This provides a seal between the first oscillating housing 7 and the first carrier 31 (rotating portion 3).

[0054] A first carrier-side second labyrinth portion 37 having a smaller outer diameter is formed on the outer circumferential edge of the second end portion 35b of the disk portion 35, with a step interposed between them. A first labyrinth 38 is formed by this first carrier-side second labyrinth portion 37 and the first carrier-side first labyrinth portion 16 formed in the first oscillating housing 7. Because the first labyrinth 38 is disposed radially outward of the seal portion 15, it is possible to reliably prevent the intrusion of dust and other foreign matter from the outside between the first oscillating housing 7 and the first carrier 31 (rotating portion 3).

[0055] An outer flange portion 39 that protrudes radially outward is formed on the outer peripheral surface 35c of the disc portion 35. The outer flange portion 39 is for attaching the hydraulic motor 1 to an external device (not shown). Through holes 39a for passing bolts (not shown) are formed in the outer flange portion 39 in the thickness direction (axial direction) of the outer flange portion 39.

[0056] A plurality of (for example, three in this embodiment) shaft support recesses 44 are formed at equal intervals in the circumferential direction near the outer periphery (slightly radially inward of the first outer periphery surface 33d) of the second end 33b of the base plate portion 33. The shaft support recesses 44 rotatably support the crankshaft 4. A first bearing 59a for rotatably supporting the crankshaft 4 is fitted into the shaft support recess 44. The first bearing 59a is, for example, a plain bearing. However, the first bearing 59a is not limited to this, and various bearings such as a ball bearing can be used.

[0057] In addition, in the base plate portion 33, a plurality of supply passages 41, a plurality of discharge passages 42, and a drain passage (tank passage) 43 are formed radially inward of the second outer peripheral surface 33e over the entire axial direction of the base plate portion 33. The supply passages 41 are oil passages (flow paths) to which hydraulic oil is supplied from a hydraulic pump (not shown). The second direction ends of the supply passages 41 open through the large step portions 33h. That is, each supply passage 41 has a supply opening 41a in the large step portion 33h. The discharge passages 42 are oil passages (flow paths) through which hydraulic oil is discharged from the hydraulic motor 1. The second direction side ends of the discharge passages 42 also open through the large step portions 33h. That is, each discharge passage 42 has a discharge opening 42a in the large step portion 33h.

[0058] The number of supply paths 41 and the number of discharge paths 42 each differ from the number of through holes 46a in the supply / discharge plate 46 fixed to the first swing housing 7. For example, in this embodiment, the number of supply paths 41 and the number of discharge paths 42 are each 12, which is one less than the number of through holes (supply / discharge ports) 46a in the supply / discharge plate 46. The supply openings 41a of the supply passage 41 and the discharge openings 42a of the discharge passage 42 are arranged alternately in the circumferential direction on the same pitch circle. Each supply opening 41a and each discharge opening 42a are paired and arranged at equal intervals in the circumferential direction.

[0059] The drain passage (tank passage) 43 is a flow path for returning the hydraulic oil leaking from the hydraulic motor 1 to a tank (not shown). The first direction side ends of the supply passage 41, the discharge passage 42, and the drain passage 43 communicate with the oil distribution section 45 via a distribution plate 100 provided at the first end 33a on the first direction side of the base plate section 33. The distribution plate 100 has flow paths 103 to 107 that can distribute oil into a plurality of flow paths, as will be described later. The oil distribution section 45 has a plurality of flow paths 111 to 114, as will be described later. The distribution plate 100 is in contact with the first end 35a on the first direction side of the disc section 35.

[0060] Hydraulic oil from the hydraulic pump is supplied to the flow paths 103 to 107 via a plurality of flow paths 111 to 114. Hydraulic oil from the flow paths 111 to 114 is supplied to the supply path 41 via these distributable flow paths 103 to 107. Furthermore, the hydraulic oil discharged to the discharge passage 42 is returned to the tank via the distributable flow paths 103-107 and flow paths 111-114 or is returned to the supply passage 41 again. The hydraulic oil discharged to the drain passage 43 may also be returned to the tank via the distribution flow paths. The action of the hydraulic oil will be described in detail later.

[0061] A gap is formed between the large step portion 33h of the first carrier 31 and the supply / discharge plate (port plate) 46. A sliding plate (piston plate) 50 is disposed in this gap. The sliding plate 50 is formed in an annular shape when viewed in the axial direction. The sliding plate 50 has its inner peripheral surface fitted into the first outer peripheral surface 33d of the first carrier 31, and is provided so as to be non-rotatable relative to the first carrier 31 and slidable in the direction of the axis C1. The thickness of the sliding plate 50 is smaller than the gap between the large step portion 33h and the supply / discharge plate 46.

[0062] A plurality of through holes (through ports) 50c are formed in the sliding plate (piston plate) 50 so as to correspond to the supply opening 41a of the supply passage 41 and the discharge opening 42a of the discharge passage 42. The through hole 50c corresponding to the supply opening 41a is arranged coaxially with the supply opening 41a. The through hole 50c corresponding to the discharge opening 42a is arranged coaxially with the discharge opening 42a.

[0063] Each supply opening 41a and each discharge opening 42a is provided with a cylindrical piston 51. The piston 51 is provided so as to be slidable in the supply passage 41 and the discharge passage 42. The piston 51 is biased toward the sliding plate 50 by a spring 51s provided in the supply passage 41 and the discharge passage 42. Therefore, the piston 51 is pressed against the sliding plate (piston plate) 50.

[0064] The thickness of the sliding plate 50 is smaller than the gap between the large step portion 33h and the supply / discharge plate 46. Therefore, the piston 51 protrudes from the large step portion 33h by the spring 51s and abuts against the sliding plate 50. As a result, the second direction side surface 50b of the sliding plate (piston plate) 50 is pressed against the supply / discharge plate 46. This allows each supply passage 41 to communicate with the through hole 50c of the sliding plate 50 via the piston 51. Also, each discharge passage 42 to communicate with the through hole 50c of the sliding plate 50 via the piston 51. Furthermore, each through hole 50c of the sliding plate 50 communicates with the through hole 46a of the supply / discharge plate 46.

[0065] The support columns 34 of the first carrier 31 are pillars formed in a triangular shape when viewed in the axial direction. Each support column 34 is arranged so as to be located between the shaft support recesses 44 of the base plate 33 in the circumferential direction. In other words, the support columns 34 are arranged at equal intervals in the circumferential direction on the second end 33b of the base plate 33. The pitch circle diameter of each support column 34 and the pitch circle diameter of the shaft support recesses 44 are approximately the same.

[0066] The tip end 34a of the support column 34 is formed flat. The tip end 34a of the support column 34 is located on the same plane as the second end 7d of the first swing housing 7. A female thread portion 52 for a reamer bolt is formed on the tip end 34a of the support column 34.

[0067] The reamer bolt female thread portion 52 comprises a fitting recess 52a formed along the axial direction from the tip end 34a of the support portion 34 to the axial center of the support portion 34, and a female thread portion main body 52b extending in the first direction from the bottom of the fitting recess 52a. By fastening a reamer bolt (an example of another fixing portion) 53 into the reamer bolt female thread portion 52, the first carrier 31 and the second carrier 32 are integrated.

[0068] The second carrier 32 is formed in a disk shape. The second carrier 32 is positioned so that a first end 32a on the first direction side abuts against a tip end 34a of a support portion 34 constituting the first carrier 31. As a result, a gap equal to the height of the support portion 34 is formed between the base portion 33 of the first carrier 31 and the second carrier 32. The thick portion 10 of the first oscillating housing 7 surrounds the periphery of this gap, thereby forming an oscillating gear storage portion 60 for storing the oscillating gear 5.

[0069] The first end 32a of the second carrier 32 is formed flat over its entirety. A fitting hole 54 penetrating the second carrier 32 in the thickness direction is formed at a position corresponding to the reamer bolt female thread portion 52. A reamer bolt 53 is inserted into the fitting hole 54 from the second direction side of the second carrier 32, and the reamer bolt 53 is tightened into the female thread portion main body 52b via the fitting recess 52a of the support portion 34, thereby integrating the first carrier 31 and the second carrier 32.

[0070] The reamer bolt 53 comprises a shaft 53a, a male threaded portion 53b that protrudes from the first side end of the shaft 53a and is formed coaxially with the shaft 53a, and a head 53c that is formed coaxially with the shaft 53a at the second side end of the shaft 53a. When the reamer bolt 53 is fastened to the reamer bolt female threaded portion 52, the shaft 53a of the reamer bolt 53 is fitted into the fitting recess 52a of the support portion 34 and the fitting hole 54 of the second carrier 32. In other words, the shaft 53a of the reamer bolt 53 is disposed across the first carrier 31 and the second carrier 32.

[0071] At the second end 32b on the second direction side of the second carrier 32, a counterbore 55 is formed in the fitting hole 54. The head 53c of the reamer bolt 53 is inserted into the counterbore 55. This reduces the protrusion height of the head 53c of the reamer bolt 53 from the second end 32b of the second carrier 32.

[0072] The outer peripheral surface 32c of the second carrier 32 has a reduced diameter portion 56 formed with a smaller outer diameter via a step portion 56a in most of the axial center. An inner race 13b of the second bearing 13 is fitted into this reduced diameter portion 56. As a result, the second carrier 32 is rotatably supported relative to the second swing housing 8 via the second bearing 13.

[0073] A second carrier-side second labyrinth portion 57 is formed on the first direction side of the location of the reduced diameter portion 56 where the second bearing 13 is fitted. The second carrier-side second labyrinth portion 57 is formed by making the outer diameter smaller than the outer diameter of the reduced diameter portion 56 via a step portion 57a. The outer diameter of the second carrier-side second labyrinth portion 57 is slightly smaller than the inner diameter of the second carrier-side first labyrinth portion 25 of the second oscillating housing 8.

[0074] The tip of the second carrier-side second labyrinth portion 57 is located slightly before the step portion 25a of the second carrier-side first labyrinth portion 25. In this manner, the second carrier-side first labyrinth portion 25 of the second swing housing 8 and the second carrier-side second labyrinth portion 57 of the second carrier 32 form the second labyrinth 40.

[0075] A plurality of (for example, three in this embodiment) shaft support holes 58 are formed at equal intervals in the circumferential direction slightly radially inward of the second carrier-side second labyrinth portion 57 of the second carrier 32. The shaft support holes 58 rotatably support the crankshaft (eccentric rotor) 4. These shaft support holes 58 and the corresponding shaft support recesses 44 of the first carrier 31 are positioned coaxially. A second bearing 59b is fitted into the shaft support hole 58. The second bearing 59b is, for example, a plain bearing. However, the second bearing is not limited to this, and various bearings such as a ball bearing can be used.

[0076] <Crankshaft> Each crankshaft 4 is rotatably supported in the shaft support recess 44 and the shaft support hole 58 via each bearing 59a, 59b. It can be said that the crankshaft 4 is slidably rotatable in the shaft support recess 44 and the shaft support hole 58 via the bearings 59a, 59b. In this embodiment, the number of crankshafts 4 is three. Each crankshaft 4 is integrally formed with bearing portions 4a, 4b (first bearing portion 4a, second bearing portion 4b) rotatably supported in the shaft support recess 44 and the shaft support hole 58 via bearings 59a, 59b, and a cylindrical eccentric portion 4c provided between the bearing portions 4a, 4b.

[0077] The rotational axis (second axis C2) of the crankshaft 4, i.e., the axis of each bearing 4a, 4b, is parallel to the first axis C1. Movement of the crankshaft 4 in the axial direction is restricted by thrust bearings 61a, 61b (first thrust bearing 61a, second thrust bearing 61b) provided axially outward of each bearing 4a, 4b, a first collar 70a provided in the shaft support recess 44 of the first carrier 31, and a second collar 70b provided in the shaft support hole 58 of the second carrier 32. Of the two thrust bearings 61a, 61b, the second thrust bearing 61b provided in the shaft support hole 58 of the second carrier 32 has its movement in the second direction restricted by a retaining ring 62 provided in the shaft support hole 58.

[0078] The axial length of the eccentric portion 4c is formed to be a length that fits within the axial width of the oscillating gear storage portion 60. Specifically, the axial length of the eccentric portion 4c is slightly shorter than the axial length of the thick-walled portion 10 of the first oscillating housing 7. Therefore, the position of the end of the eccentric portion 4c in the second direction and the position of the first end 8b of the second oscillating housing 8 are on approximately the same plane. The axis of the eccentric portion 4c (third axis C3) is eccentric with respect to the second axis C2 of the crankshaft 4. The oscillating gear 5 is rotatably supported by this eccentric portion 4c via a third bearing 59c. The third bearing 59c is, for example, a sliding bearing. However, the third bearing is not limited to this, and various bearings such as a ball bearing can be used.

[0079] The outer diameter of the oscillating gear 5 is smaller than the diameter of the inner peripheral surface 10d of the thick-walled portion 10 so that it can be housed in the oscillating gear housing portion 60. The axial thickness of the oscillating gear 5 is equal to that of the eccentric portion 4c. Therefore, the position of the end of the oscillating gear 5 in the second direction and the position of the first end 8b of the second oscillating housing 8 are on approximately the same plane. A support hole 63, through which the eccentric portion 4c of the crankshaft 4 passes, is formed in the oscillating gear 5 at a position corresponding to the crankshaft 4.

[0080] The support holes 63 are arranged at equal intervals in the circumferential direction. Third bearings 59c are provided in these support holes 63. Axial movement of the oscillating gear 5 relative to the crankshaft 4 is restricted by snap rings 67 provided on both axial ends of the third bearing 59c. With this configuration, the rotation of the oscillating gear 5 is restricted to oscillating rotation by the crankshaft 4.

[0081] Furthermore, the oscillating gear 5 is formed with relief holes 64, through which the support pillars 34 pass, at positions corresponding to the support pillars 34 of the first carrier 31. The shape of the relief holes 64 as viewed in the axial direction is triangular, corresponding to the shape of the support pillars 34 as viewed in the axial direction. The size of the relief holes 64 is formed to be sufficiently larger than the outer surface shape of the support pillars 34 so that each support pillar 34 does not interfere with the oscillating rotation of the oscillating gear 5.

[0082] The outer peripheral surface of the oscillating gear 5 faces the internally toothed pin 90 of the first oscillating housing 7 in the radial direction. External teeth 65 that mesh with the internally toothed pin 90 are formed on the outer peripheral surface of the oscillating gear 5. The number of teeth of the external teeth 65 is different from the number of teeth (number) of the internally toothed pin 90. For example, in this embodiment, the number of teeth of the external teeth 65 is 12, which is one less than the number of teeth of the internally toothed pin 90. This number matches the number of supply paths 41 and discharge paths 42 formed in the first carrier 31.

[0083] During oscillating rotation, the oscillating gear 5 is always in contact with the internal tooth pin 90 somewhere between the tooth tip 65a and the tooth bottom 65b. As a result, two major working chambers 66a, 66b (first working chamber 66a and second working chamber 66b) are formed between the inner peripheral surface 10d of the thick-walled portion 10 formed in the first oscillating housing 7 and the external teeth 65 of the oscillating gear 5. The two working chambers 66a, 66b are formed line-symmetrically when viewed from the axial direction. An operating chamber 66c is formed between the operating chambers 66a and 66b. Here, the operating chambers 66a and 66b are distinguished according to the pressure state during operation. As will be described later, the position that is connected to the supply path 41 and becomes high pressure is referred to as the operating chamber 66a, and the position that is connected to the discharge path 42 and becomes low pressure is referred to as the operating chamber 66b. Therefore, the position that becomes pressure when not connected to both the supply path 41 and the discharge path 42 at the same time is referred to as the operating chamber 66c.

[0084] These working chambers 66a, 66b are connected to a plurality of through holes (supply / discharge ports) 46a in a supply / discharge plate (port plate) 46. Hydraulic oil is supplied to and discharged from the working chambers 66a, 66b via these through holes 46a, thereby driving and rotating the hydraulic motor 1.

[0085] <Distribution board> The distribution plate 100 is sandwiched in the thickness direction with end faces 101, 102 in contact with the oil distribution section 45 and the disc section 35, respectively, and has third flow paths 103-107 connecting the first flow paths 111-114 and the supply and discharge flow paths (second flow paths) 41, 42. The distribution plate 100 is sandwiched between the oil distribution section 45, which is the first housing, and the rotating section 3 and oscillating housing section 2, which is the second housing, including the disc section 35, and the third flow paths 103-107 divide and merge the hydraulic oil (fluid) between the first flow paths 111-114 and the second flow paths 41, 42.

[0086] An end face 101 of the distribution plate 100 in the first direction is in contact with an end face 45a of the oil distribution portion 45, which is the first housing. An end face 102 of the distribution plate 100 in the second direction is in contact with a first end portion 35a on the first direction side of the disc portion 35, which is the second housing. The distribution plate 100 is pressed by the end faces 45a and the first end portion 35a on both the front and back sides of the end faces 101, 102, to maintain a sealed state. The distribution plate 100 can also be pressed by fastening the oil distribution portion 45, which is the first housing, and the disk portion 35, which is the second housing.

[0087] The distribution plate 100 is formed with a plurality of through-flow passages 103 as third flow passages, penetrating the plate in the thickness direction and opening at the end face 101 and the end face 102. The plurality of through-flow passages 103 are arranged in a circumferential direction on the same circumference centered on the axis C1 on the end face 101 and the end face 102. The opening positions of the plurality of through-flow passages 103 are spaced apart at equal intervals in the circumferential direction. The number of through-flow passages 103 is equal to the total number of supply passages 41 and discharge passages 42. The number of through-flow passages 103 is arranged to correspond to the number of pistons 51. In this embodiment, 24 through-flow passages 103 are arranged in a circumferential direction.

[0088] The openings of the end face 101 of the plurality of through-flow passages 103 are opposite and connected to the first flow passages 111-114 that open to the end face 45a of the oil distribution part 45, which is the first housing. Note that the end face 101 does not need to have openings that connect all of the through-flow passages 103 and the first flow passages 111-114 opposite to each other. The openings of the plurality of through-flow passages 103 in the end face 102 face and connect to the supply passages 41 and the discharge passages 42 that open to the first end 35a on the first direction side of the disk portion 35, which is the second housing. In the end face 102, the through-flow passages 103 have openings that face and connect to the corresponding supply passages 41 or discharge passages 42, respectively.

[0089] On the end face 101 of the distribution plate 100, as third flow paths, there are formed groove-like connecting groove flow paths which connect a plurality of through flow paths 103, namely, an outer peripheral connecting groove flow path 104, an inner peripheral connecting groove flow path 105, an outer radial groove flow path 106, and an inner radial groove flow path 107. The outer periphery connecting groove channel 104 is formed as an annular groove along the circumferential direction of the distribution plate 100, radially outward of the multiple through-flow channels 103 that open to the end face 101. The outer periphery connecting groove channel 104 has the same width dimension and the same depth dimension all around.

[0090] The inner circumferential connecting groove channel 105 is formed as an annular groove radially inward of the multiple through-flow channels 103 that open to the end face 101 along the circumferential direction of the distribution plate 100. The inner circumferential connecting groove channel 105 has the same width dimension and the same depth dimension all around. The outer circumferential connecting groove passage 104 and the inner circumferential connecting groove passage 105 have the same width and depth dimensions. The outer circumferential connecting groove passage 104 and the inner circumferential connecting groove passage 105 are arranged concentrically about the axis C1.

[0091] The outer radial groove 106 is formed in the end face 101 along the radial direction of the distribution plate 100 in a groove shape so as to connect a through-passage 103 at a predetermined position among the plurality of through-passages 103 arranged in the circumferential direction to the outer periphery connecting groove 104. The inner radial groove 107 is formed in the end face 101 along the radial direction of the distribution plate 100 in a groove shape so as to connect a through-passage 103 at a predetermined position among the plurality of through-passages 103 arranged in the circumferential direction to the inner periphery connecting groove 105.

[0092] Similarly to the end face 101, an end face 102 of the distribution plate 100 is also formed with groove-like connecting groove channels, namely, an outer circumferential connecting groove channel 104, an inner circumferential connecting groove channel 105, an outer radial direction groove channel 106, and an inner radial direction groove channel 107, as connecting groove channels that connect a plurality of through-flow channels 103. On the end face 101 and the end face 102, the outer circumferential connecting groove channel 104 and the inner circumferential connecting groove channel 105 have substantially the same shape and are arranged symmetrically in the thickness direction. Furthermore, the outer radial grooves 106 and the inner radial grooves 107 are formed to have substantially the same shapes on the end faces 101 and 102. However, the circumferential arrangements of the outer radial grooves 106 and the inner radial grooves 107 are different on the end faces 101 and 102.

[0093] In this embodiment, six through-passages 103 are connected to the outer periphery connecting groove passage 104 of the end face 101 via outer radial groove passages 106. Six through-passages 103 are connected to the inner periphery connecting groove passage 105 of the end face 101 via inner radial groove passages 107. Six through-passages 103 are connected to the outer periphery connecting groove passage 104 of the end face 102 via outer radial groove passages 106. Six through-passages 103 are connected to the inner periphery connecting groove passage 105 of the end face 102 via inner radial groove passages 107.

[0094] The outer peripheral connecting groove passage 104 of the end face 101, the inner peripheral connecting groove passage 105 of the end face 101, the outer peripheral connecting groove passage 104 of the end face 102, the inner peripheral connecting groove passage 105 of the end face 102, and the through passage 103 connected thereto are separated from one another and form four separate passages. These four passages formed in the distribution plate 100 correspond to the four first passages 111-114 formed in the oil distribution section 45, which is the first housing. Note that Figures 5 to 7 show the mutual correspondence between the four independent passages in the distribution plate 100 and the four first passages 111-114.

[0095] As the four independent flow paths, any one of the inner radial groove flow paths 107 of the end face 101, the outer radial groove flow paths 106 of the end face 101, the inner radial groove flow paths 107 of the end face 102, and the outer radial groove flow paths 106 of the end face 102 is formed in the through flow paths 103. Moreover, no two or more of the inner radial groove flow paths 107 of the end face 101, the outer radial groove flow paths 106 of the end face 101, the inner radial groove flow paths 107 of the end face 102, and the outer radial groove flow paths 106 of the end face 102 are formed in the same through flow path 103.

[0096] In this way, of the through-passages 103 lined up in the circumferential direction, four adjacently opening through-passages 103 are considered as a group, and the arrangement of the outer radial grooves 106 and the inner radial grooves 107 in the end faces 101 and 102 is repeated in the circumferential direction. In other words, the inner radial grooves 107 in the end face 101, the outer radial grooves 106 in the end face 101, the inner radial grooves 107 in the end face 102, and the outer radial grooves 106 in the end face 102 are considered as a group, and this group is repeated in the circumferential direction. Alternatively, the radially inner grooves 107 on the end face 101, the radially inner grooves 107 on the end face 102, the radially outer grooves 106 on the end face 101, and the radially outer grooves 106 on the end face 102 can be used as a set and this set can be repeated in the circumferential direction. Furthermore, by reversing the circumferential arrangement direction of these grooves, i.e., whether clockwise or counterclockwise in plan view, yet another repeating pattern can be created.

[0097] The configuration exemplified in this embodiment is as follows. The flow passages 111 are connected to the radially inner groove flow passages 107 in the end face 102. The flow passages 112 are connected to the radially outer groove flow passages 106 in the end face 102. The flow passages 113 are connected to the radially inner groove flow passages 107 in the end face 101. The flow passages 114 are connected to the radially outer groove flow passages 106 in the end face 101. That is, when the flow paths 111 to 114 are set to different pressure states, the pressure states of the four independent flow paths can be made to correspond to those pressure states.

[0098] The opening of the through passage 103 in the end face 102 is connected to the supply passage 41 and the discharge passage 42 formed in the disk portion 35 and the base plate portion 33, which form the second housing. Of the four independent passages described above, two are connected to the supply passage 41 and two are connected to the discharge passage 42. The action of the hydraulic oil will be described in detail later. The operation of the hydraulic motor 1 will be described in detail below.

[0099] <Hydraulic motor operation> Next, the operation of the hydraulic motor 1 will be described. In the hydraulic motor 1 , hydraulic oil is supplied from a hydraulic pump (not shown) to each supply passage 41 via the flow paths 111 , 113 of the oil distribution section 45 and the distribution plate 100 .

[0100] 5 to 7, hydraulic oil supplied from the hydraulic pump is sent through the flow passages 111 and flows into the distribution plate 100 from the openings in the end face 45a of the flow passages 111. The hydraulic oil that has flowed into the distribution plate 100 flows from the inner radial groove flow passages 107 in the end face 101 to the inner circumferential connecting groove flow passages 105 in the end face 101 via the through passages 103 in the end face 101 that open opposite the openings in the end face 45a of the flow passages 111.

[0101] In the distributor plate 100, in the inner circumferential connecting groove passage 105 on the end face 101, the hydraulic oil is diverted from the inner radial groove passage 107 on the other end face 101 that is connected to this inner circumferential connecting groove passage 105 to the other through-passages 103. In the distributor plate 100 of this embodiment, the hydraulic oil is distributed to five through-passages 103. The distributed hydraulic oil further flows in the thickness direction of the distributor plate 100 in these through-passages 103 and is supplied to each supply path 41 via the openings of the through-passages 103 on the end face 102.

[0102] Similarly, as shown in Figures 5 to 7, hydraulic oil supplied from a hydraulic pump is sent through flow passages 113 and flows into the distribution plate 100 from openings in the end face 45a of the flow passages 113. The hydraulic oil that has flowed into the distribution plate 100 flows into through-passages 103 in the end face 101 that open opposite the openings in the end face 45a of the flow passages 113, and flows in the through-passages 103 in the thickness direction of the distribution plate 100. Furthermore, the hydraulic oil flows into the inner peripheral connecting groove passages 105 in the end face 102 of the through-passages 103 via the inner radial groove passages 107 in the end face 102.

[0103] In the distributor plate 100, in the inner circumferential connecting groove passage 105 on the end face 102, the hydraulic oil is diverted from the inner radial groove passage 107 on the other end face 102 that is connected to this inner circumferential connecting groove passage 105 to other through-passages 103. In the distributor plate 100 of this embodiment, the hydraulic oil is distributed to five through-passages 103. The distributed hydraulic oil is further supplied to each supply path 41 via the openings in the end face 102 of these through-passages 103.

[0104] The hydraulic oil is supplied at the same pressure P1 through the plurality of supply paths 41 and the flow paths 111, 113. In Figures 5 to 7 and 11, the hydraulic oil (fluid) being supplied is in a high-pressure state, which is indicated by P1. The hydraulic oil supplied to each supply passage 41 is supplied to the operating chambers 66a, 66b via the piston 51 of each supply opening 41a, the through hole (through port) 50c of the sliding plate (piston plate) 50, and the through hole (supply / discharge port) 46a of the supply / discharge plate (port plate) 46.

[0105] Here, the piston 51 of each supply opening 41a is biased toward the sliding plate 50 by a spring 51s and slides on the sliding plate (piston plate) 50, which rotates integrally with the first carrier 31. When the through hole (through port) 50c comes to a position aligned with the piston 51 due to the rotation of the sliding plate 50, the hydraulic oil supplied to the supply passage 41 flows into the through hole (through port) 50c.

[0106] A sliding plate (piston plate) 50, which rotates integrally with the first carrier 31, slides on a supply / discharge plate (port plate) 46, which is integral with the oscillating housing portion 2. When the through hole (supply / discharge port) 46a comes to a position aligned with the through hole (through port) 50c due to the rotation of the sliding plate 50 and the supply / discharge plate 46, the hydraulic oil supplied to the through hole (through port) 50c flows into the through hole (supply / discharge port) 46a. Furthermore, when the through hole (supply / discharge port) 46a and the through hole (through port) 50c are not aligned and connected, the sliding plate (piston plate) 50 blocks the through hole (supply / discharge port) 46a, preventing the hydraulic oil from leaking or flowing back from the working chambers 66a, 66b through the through hole (supply / discharge port) 46a.

[0107] Here, the number of supply paths 41 (supply openings 41a and through holes 50c of the sliding plate 50 communicating with the supply openings 41a) is one less than the number of through holes 46a of the supply / discharge plate 46. Also, the number of discharge paths 42 (discharge openings 42a and through holes 50c of the sliding plate 50 communicating with the discharge openings 42a) is one less than the number of through holes 46a of the supply / discharge plate 46. Therefore, only the supply path 41 communicates with either one of the two working chambers 66a, 66b via the through hole 46a of the supply / discharge plate 46. Also, only the discharge path 42 communicates with the other of the two working chambers 66a, 66b via the through hole 46a of the supply / discharge plate 46. At this time, the through-hole 46a of the supply / discharge plate 46 in the working chamber 66c does not communicate with the through-hole 50c of the sliding plate 50, so the supply path 41 and the discharge path 42 do not communicate with the working chamber 66c.

[0108] As a result, the pressure inside one of the two working chambers 66a, 66b becomes higher than the pressure inside the other of the two working chambers 66a, 66b. For ease of understanding, the following description will be given assuming that the pressure P1 in the working chamber 66a (left side in FIG. 2) of the two working chambers 66a, 66b becomes higher than the pressure P2 in the working chamber 66b (right side in FIG. 2). In addition, in the following description, the working chamber 66a with the higher pressure P1 will be referred to as the high-pressure working chamber 66a. The working chamber 66b with the lower pressure P2 compared to the high-pressure working chamber 66a will be referred to as the low-pressure working chamber 66b. The high-pressure working chamber 66a communicates with the supply path 41. The low-pressure working chamber 66b communicates with the discharge path 42. The hydraulic oil flows at the same pressure P2 in all the discharge passages 42. In addition, in Figures 5 to 7 and 11, the discharged hydraulic oil (fluid) is in a low pressure state, which is indicated by P2.

[0109] When hydraulic oil is supplied to the high-pressure operating chamber 66a, the oscillating gear 5 is pressed toward the low-pressure operating chamber 66b (see arrow Y1 in FIG. 2). The hydraulic oil in the low-pressure operating chamber 66b is discharged through the discharge path 42. As a result, the internal pin 90 and the external teeth 65 of the oscillating gear 5 mesh on the low-pressure operating chamber 66b side. Then, because the number of teeth of the external teeth 65 is one less than the number of teeth of the internal pin 90, the oscillating gear 5 shifts slightly in the rotational direction.

[0110] At this time, the carrier portion 6 is shifted in the rotational direction along with the oscillating gear 5 via the crankshaft 4. That is, the rotating portion 3 is rotated slightly relative to the oscillating housing portion 2. This causes the sliding plate 50 to rotate relative to the supply / discharge plate 46. This switches the state in which the through hole 50c of the sliding plate 50 and the through hole 46a of the supply / discharge plate 46 are in communication with each other. As the oscillating gear 5 rotates, the high-pressure operating chamber 66a and the low-pressure operating chamber 66b are also shifted slightly in the rotational direction.

[0111] When the communication state between the through-hole 50c of the sliding plate 50 and the through-hole 46a of the supply / discharge plate 46 switches, hydraulic oil is again supplied to the high-pressure operating chamber 66a. Also, hydraulic oil is discharged from the low-pressure operating chamber 66b. By repeating this process in sequence, the rotating part 3 rotates relative to the oscillating housing part 2. This rotation generates output.

[0112] Here, when the through hole (supply / discharge port) 46a comes to a position aligned with the through hole (through port) 50c due to the rotation of the sliding plate 50 and the supply / discharge plate 46, the hydraulic oil is discharged from the low-pressure operating chamber 66b into the through hole (through port) 50c. Furthermore, when the through hole (supply / discharge port) 46a and the through hole (through port) 50c are not aligned and connected, the sliding plate (piston plate) 50 blocks the through hole (supply / discharge port) 46a, preventing hydraulic oil from being discharged from the working chambers 66a, 66b through the through hole (supply / discharge port) 46a.

[0113] The piston 51 in the discharge opening 42a of the discharge passage 42 is biased toward the sliding plate 50 by a spring 51s and slides on the sliding plate (piston plate) 50, which rotates integrally with the first carrier 31. When the through hole (through port) 50c comes to a position aligned with the piston 51 due to the rotation of the sliding plate 50, the hydraulic oil discharged from the through hole (supply / discharge port) 46a flows through the piston 51 in the discharge opening 42a into the discharge passage 42 and the discharged hydraulic oil into each discharge passage 42 is returned to the tank via the distribution plate 100 and the flow paths 112, 114 of the oil distribution unit 45.

[0114] 5 to 7, the hydraulic oil discharged to each discharge passage 42 flows into the distribution plate 100 from the openings at the first end 35a of the disk portion 35. The hydraulic oil flows into the through passages 103 through the openings at the end face 102 that face the openings at the first end 35a.

[0115] Among the through-flow passages 103, in the through-flow passage 103 having the outer peripheral connecting groove passage 104 on the end face 102, the hydraulic oil flowing in from the corresponding discharge passage 42 flows through the through-flow passage 103 from the outer radial groove passage 106 on the end face 102 to the outer peripheral connecting groove passage 104 on the end face 102 and joins there. In the distribution plate 100, the hydraulic oil that joins in the outer peripheral connecting groove channels 104 on the end face 102 flows into the through channels 103 that communicate with the channels 112 on the end face 101. In the distribution plate 100 of this embodiment, the hydraulic oil joins from the five through channels 103 to the through channel 103 that communicates with the channel 112 via the outer peripheral connecting groove channels 104 on the end face 102.

[0116] The hydraulic oil flows in the through-flow passages 103 in the thickness direction of the distribution plate 100, and is further discharged from the through-flow passages 103 opening at the end face 101 to the passages 112 via the opening at the end face 45a.

[0117] Similarly, in the through-flow passages 103 having the outer peripheral connecting groove passages 104 on the end face 101, the hydraulic oil flowing in from the corresponding discharge passages 42 flows in the thickness direction of the distribution plate 100 through the through-flow passages 103. The hydraulic oil that reaches the end face 101 flows through the through-flow passages 103 from the outer radial groove passages 106 on the end face 101 to the outer peripheral connecting groove passages 104 on the end face 101 and joins there. In the distribution plate 100 of this embodiment, the hydraulic oil joins through the outer peripheral connecting groove passages 104 on the end face 101 from the five through-flow passages 103 to the through-flow passages 103 that communicate with the passage 114.

[0118] In the distribution plate 100 , the hydraulic oil that joins in the outer circumferential connecting groove flow passage 104 on the end face 101 flows into the through flow passage 103 that communicates with the flow passage 114 on the end face 101 . The hydraulic oil is further discharged from the through passage 103 opening at the end face 101 to the passage 114 via the opening at the end face 45a.

[0119] The hydraulic oil is discharged at the same pressure P2 from the plurality of discharge paths 42 and the flow paths 112, 114. In Figures 5 to 7 and 11, the hydraulic oil (fluid) being supplied is in a low pressure state, which is indicated by P2. In this way, the hydraulic oil discharged from the working chamber 66b through each discharge passage 42 joins at the distribution plate 100 and is discharged into the passages 112 and 114.

[0120] In this way, the hydraulic motor 1 utilizes the mismatch between the number of supply paths 41 (the supply openings 41a and the through holes 50c of the sliding plate 50 communicating with the supply openings 41a) and the number of through holes 46a of the supply / discharge plate 46, and the mismatch between the number of discharge paths 42 (the discharge openings 42a and the through holes 50c of the sliding plate 50 communicating with the discharge openings 42a) and the number of through holes 46a of the supply / discharge plate 46, so that the state in which the through holes 50c of the sliding plate 50 communicate with the through holes 46a of the supply / discharge plate 46 are communicated with sequentially in the circumferential direction. As a result, hydraulic oil is selectively supplied to and discharged from each of the through holes 46a of the supply / discharge plate 46 to each of the working chambers 66a, 66b, and the rotating part 3 is rotated.

[0121] The carrier unit 6 that constitutes the rotating unit 3 is divided into a first carrier 31 and a second carrier 32. The first carrier 31 and the second carrier 32 are fixed together by a reamer bolt 53, and power is transmitted between the first carrier 31 and the second carrier 32 via the reamer bolt 53. A shaft portion 53a of the reamer bolt 53 is disposed across the first carrier 31 and the second carrier 32. Therefore, power is transmitted between the first carrier 31 and the second carrier 32 more efficiently than when the male thread portion 53b is disposed across the first carrier 31 and the second carrier 32.

[0122] Furthermore, the hydraulic oil supplied to each working chamber 66a, 66b leaks out into the minute gap between each carrier 31, 32 and the crankshaft 4 via the minute gap between the crankshaft 4 and the oscillating gear 5. This leaked hydraulic oil is discharged into the drain passage (tank path) 43 via the shaft support recess 44 formed in the first carrier 31. The hydraulic oil discharged into the drain passage (tank path) 43 is returned to a tank (not shown).

[0123] Here, on the first direction side of the oscillating gear 5, a third labyrinth 49 is formed by the first outer peripheral surface 33d and the second end portion 33b of the first carrier 31, and the plate-side labyrinth portion 48 of the supply / discharge plate 46. On the second direction side of the oscillating gear 5, a second labyrinth 40 is formed by the second-carrier-side first labyrinth portion 25 of the second oscillating housing 8 and the second-carrier-side second labyrinth portion 57 of the second carrier 32. For this reason, hydraulic oil leaking from the working chambers 66a, 66b through the minute gap between the crankshaft 4 and the oscillating gear 5 is less likely to leak out from between the first oscillating housing 7 and the first carrier 31 and between the second oscillating housing 8 and the second carrier 32.

[0124] In the hydraulic motor 1, by fixing the oscillating housing portion 2, it is possible to obtain output from the rotating portion 3. In this case, an external device fixed to the outer flange portion 39 of the rotating portion 3 (first carrier 31) becomes the rotated body. In addition, by fixing the rotating portion 3, it is also possible to obtain output from the oscillating housing portion 2. In this case, an external device fixed to the outer flange portion 9 of the oscillating housing portion 2 (first oscillating housing 7) becomes the rotated body.

[0125] The hydraulic motor 1 has an internally toothed pin 90 provided in the first oscillating housing 7. The rotating section 3 includes a carrier section 6, a crankshaft 4 rotatably supported on the carrier section 6, and an oscillating gear 5 that is oscillated by the crankshaft 4 and meshes with the internally toothed pin 90. With this configuration, the hydraulic motor 1 can be rotationally driven by supplying and discharging hydraulic oil to working chambers 66a, 66b formed between the inner circumferential surface 7c of the first oscillating housing 7 and the outer circumferential surface of the oscillating gear 5. This rotational drive can produce high rotational torque. A divided oscillating housing section 2 can be suitably used in such a hydraulic motor 1.

[0126] The hydraulic motor 1 has a supply / discharge plate 46 for selectively supplying and discharging hydraulic oil to each of the working chambers 66a, 66b. The supply / discharge plate 46 is disposed at the first end 10b of the thick-walled portion 10 (the end on the first direction side of the oscillating gear 5). Such a supply / discharge plate 46 is fixed to the first oscillating housing 7 using bolts 20. Because the supply / discharge plate 46 is also fixed using the bolts 20 that are used to fix the first oscillating housing 7 and the second oscillating housing 8, the number of parts of the hydraulic motor 1 can be reduced.

[0127] As described above, in the hydraulic motor 1 of the embodiment described above, the hydraulic oil supplied from the hydraulic pump to the oil distribution unit 45 is distributed to each supply path 41 at the distribution plate 100 via the flow paths 111 and 113, and is then supplied to the working chambers 66a and 66b. Furthermore, the hydraulic oil discharged from the working chambers 66a and 66b via each discharge path 42 joins together at the distribution plate 100 and is discharged to the flow paths 112 and 114.

[0128] According to the hydraulic motor 1, the distribution plate 100 has a through-flow passage 103 connecting the end face 101 and the end face 102, and connecting groove passages 104-107 formed as grooves in the end faces 101 and 102. These third passages 103-107 are sandwiched so that the end face 45a of the oil distribution section 45, which is the first housing, is in close contact with the end face 101, and the first end 35a of the disk section 35, which is the second housing, is in close contact with the end face 102, thereby sealing the grooves, thereby easily allowing the hydraulic oil (fluid) to flow through the distribution plate 100. Therefore, the distribution plate 100 connects the first passages 111-114 and the second passages 41 and 42. This distribution plate 100 allows the hydraulic oil (fluid) to be distributed and merged between the first passages 111-114 and the second passages 41 and 42, which are greater in number than the first passages 111-114.

[0129] Therefore, in the second direction and the first direction, the distribution and merging of the hydraulic oil between the first flow paths 111-114 and the second flow paths 41, 42 can be achieved simply by the thickness of the distribution plate 100. Therefore, compared to the conventional technology described above, it is possible to reduce the dimensions of the hydraulic motor 1 in the direction along the first axis C1. This makes it possible to increase the output torque of a hydraulic motor 1 of the same size. Alternatively, it is possible to reduce the size of a hydraulic motor 1 of the same output torque in the direction of the axis C1, thereby saving space.

[0130] The distribution plate 100 has connecting groove flow paths 104-107 formed on both front and back end faces 101, 102, respectively, thereby forming up to four independent flow paths for distributing and merging the hydraulic oil. This makes it possible to perform first-speed operation in which hydraulic oil is supplied from one flow path 111 to the supply path 41, and second-speed operation in which hydraulic oil is supplied from two flow paths 111, 113 to the supply path 41.

[0131] At this time, in first-speed operation, the hydraulic oil is discharged from the discharge passage 42 to one flow path 111. In second-speed operation, the hydraulic oil is discharged from the discharge passage 42 to two flow paths 113. Therefore, there is no restriction on the amount of oil that can be discharged. Furthermore, connecting groove flow paths 104 to 107 are formed on end faces 101 and 102, respectively, and a sealed flow path can be formed simply by sandwiching these. This significantly improves sealing performance compared to conventional techniques that form grooves on the circumferential surface.

[0132] In the distribution plate 100, multiple through-flow passages 103 are arranged circumferentially at equal intervals on the end faces 101 and 102, so that the through-flow passages 103 can be connected to the supply passages 41 and discharge passages 42 arranged alternately in the circumferential direction as an orbital motor.

[0133] In the distribution plate 100, a plurality of through-flow passages 103 are connected by outer circumferential connecting groove passages 104 and inner circumferential connecting groove passages 105. As a result, by simply passing the through-flow passages 103 through the flat circular plate and forming the outer circumferential connecting groove passages 104 and the inner circumferential connecting groove passages 105 in the shape of annular grooves on the flat end surface, it is possible to select the through-flow passages 103 at predetermined positions to form independent passages, and to easily separate and merge flows even when the pressures are different from each other.

[0134] Therefore, when manufacturing the distribution plate 100, the above structure can be easily formed by cutting a flat disk or by casting, etc. Also, since a high level of sealing can be maintained by sandwiching the plate between the first and second housings, there is no need to process the end faces 101, 102 with high precision.

[0135] In the distribution plate 100, by setting the positions of the through passages 103 that form the outer radial groove passages 106 and the inner radial groove passages 107 in advance, it is possible to select the through passages 103 that connect to the outer peripheral connecting groove passages 104 and the inner peripheral connecting groove passages 105, making it possible to distribute and merge the hydraulic oil as independent passages.

[0136] In particular, by connecting the outer radial groove flow passage 106 and the inner radial groove flow passage 107 to adjacent through passages 103 among the through passages 103 arranged along the circumferential direction, it is possible to configure the flow passages 111 to 114 to be connected and branched or merged in accordance with the second housing in which the supply passage 41 and the discharge passage 42, which are at different pressures, are adjacent.

[0137] Alternatively, the outer radial groove flow passages 106 and the inner radial groove flow passages 107 can be connected to every other adjacent through passages 103 among the through passages 103 lined up in the circumferential direction, so that, among the supply passage 41 and the discharge passage 42 which are at different pressures, for example, the flow passages 111, 113 can be connected to the high-pressure supply passage 41 to branch and merge on one side of the end faces 101, 102, and the low-pressure flow passages 112, 114 can be connected to branch and merge on the other side of the end faces 101, 102.

[0138] In this way, there is a degree of freedom in selecting the converging and branching flow paths depending on the formation positions of the outer radial grooves 106 and the inner radial grooves 107. In other words, four independent flow paths can be freely set and connected to the second flow path depending on the formation positions of the outer radial grooves 106 and the inner radial grooves 107.

[0139] In this case, the circumferential arrangement of the outer radial groove passages 106 and the inner radial groove passages 107 is repeated with four circumferentially adjacent through-passages 103 as a set, so that four independent passages can be freely set and connected to the second passage. Also, the circumferential arrangement of the outer radial groove passages 106 and the inner radial groove passages 107 is repeated with two circumferentially adjacent through-passages 103 as a set, so that two independent passages can be freely set on one of the end faces 101, 102 of the distribution plate 100 and connected to the second passage.

[0140] In the above embodiment, the bolts 20 are used as the fixing parts for fixing the first oscillating housing 7 and the second oscillating housing 8. The reamer bolts 53 are used as the fixing parts for fixing the first carrier 31 and the second carrier 32. However, this is not limited to this, and any fixing parts can be used as long as they can fix the oscillating housings 7 and 8 and the carriers 31 and 32 instead of the bolts 20 and the reamer bolts 53. For example, rivets or the like can be used as the fixing parts.

[0141] In the above embodiment, the supply / discharge plate 46 is fixed to the first oscillating housing 7 using the bolts 20. However, this is not limited to this, and the supply / discharge plate 46 may be fixed to the first oscillating housing 7 using a fixing member other than the bolts 20. Furthermore, the supply / discharge plate 46 does not have to be fastened together with the first oscillating housing 7 and the second oscillating housing 8. In this case, the oscillating housings 7, 8 may be integrated by providing outer flanges for fixing the oscillating housings on the outer peripheral surfaces of the oscillating housings 7, 8 and fixing the outer flanges with bolts.

[0142] In the above embodiment, the rotating part 3 has three crankshafts 4, and the oscillating gear 5 is restricted to oscillating rotation by these crankshafts 4. However, this is not limited to this, and the rotating part 3 may have at least one crankshaft 4. In this case, the crankshaft 4 is a so-called center crankshaft, in which the second axis C2 of this crankshaft 4 coincides with the first axis C1 of the rotating part 3. The rotation of the oscillating gear 5 is restricted by this center crankshaft.

[0143] In the above embodiment, the pressure state of the hydraulic oil has been described as the high pressure P1 and the low pressure P2, but it is also possible to set the pressure states in the first flow paths 111 to 114 to different values. 12, the pressure states in the flow paths 111-114 can be set to pressure P1, pressure P2, pressure P3, and pressure P4, and these can be allocated to the four through-flow paths 103 arranged in the circumferential direction of the distribution plate 100. In this case, the pressures P1, P2, P3, and P4 may all be different from one another, or two of the pressures P1, P2, P3, and P4 may be set to the same value and the remaining two may be set to three different values. Furthermore, it is also possible to set three of the pressures P1, P2, P3, and P4 to the same value and set them to two different values.

[0144] Among the embodiments disclosed in this specification, those that are comprised of multiple objects may be integrated, and conversely, those that are comprised of a single object may be separated into multiple objects. Regardless of whether they are integrated, it is sufficient that they are configured to achieve the object of the invention. [Explanation of symbols]

[0145] 1...Hydraulic motor (fluid device) 2...Swinging housing part (second housing) 3...Rotating part (second housing) 4...Crankshaft (eccentric rotor) 5...Oscillating gear 6...Carrier part (rotating member) 7...First swing housing 8...Second swing housing 12, 13...Bearings 31...First carrier (carrier) 32...Second carrier (carrier) 33... Circuit board portion (second housing) 35...Disc portion (second housing) 35a...first end 41...supply channel (second channel) 41a…Supply opening 42...Discharge channel (second flow channel) 42a…Discharge opening 45...Oil distribution section (first housing) 45a...end face 46...Supply / discharge plate (port plate) 46a...Through hole (supply / exhaust port) 50...Sliding plate (piston plate) 50c...Through hole (through port) 66a...High-pressure working chamber (first working chamber) 66b...Low pressure working chamber (second working chamber) 66c...operating chamber 90...Inner tooth pin 100...Distribution plate 101,102...end face 103~107...Third flow path 103...through flow path 104…Outer circumferential connection groove flow path (connection groove flow path) 105...Inner connecting groove channel (connecting groove channel) 106…Outer diameter groove flow path (connection groove flow path) 107…Inner diameter groove flow path (connection groove flow path) 111~114...First flow path C1…1st axis line (axis line) P1~P4...Pressure

Claims

1. a first housing having a first flow path; a second housing having more second flow paths than the first flow paths; a distribution plate that is sandwiched in a thickness direction with end surfaces thereof in contact with the first housing and the second housing, and has a third flow path that connects a predetermined one of the first flow paths and the second flow path; and The third flow path is a plurality of through-flow passages arranged side by side in a circumferential direction and opening on the end surface; a connecting groove flow path formed in a circumferential direction along the end surface and connecting the plurality of through-flow paths; and the distribution plate is sandwiched between the first housing and the second housing so as not to rotate relative to the second housing, The openings of the plurality of through-flow passages are connected to the corresponding second flow passages in a facing relationship. Fluid equipment.

2. The connecting groove flow paths are formed on the end surfaces of the distribution plate, which are the front and back surfaces of the distribution plate. The fluidic device of claim 1 .

3. The fluid device according to claim 1 or 2, wherein the plurality of through-flow passages arranged in the circumferential direction are disposed at equal intervals on the end face.

4. The connecting groove flow path is an outer circumferential connecting groove formed on the end surface along a circumferential direction and connecting the plurality of through-flow passages radially outward of the plurality of through-flow passages; an inner circumferential connecting groove flow path formed in the end surface along a circumferential direction and connecting the plurality of through-flow paths radially inward of the plurality of through-flow paths; having The fluid device according to any one of claims 1 to 3.

5. an outer radial groove formed on the end surface along a radial direction and connecting the through-flow passage and the outer circumferential connecting groove, the through-flow passage opening on the end surface; an inner radial groove flow path formed in the end surface along a radial direction and connecting the through flow path opening at the end surface and the inner circumferential connecting groove flow path; and the outer radial groove flow passage and the inner radial groove flow passage are respectively connected to the through-passages adjacent to each other in the circumferential direction, or the outer radial groove flow passage and the inner radial groove flow passage are respectively connected to the through-passages adjacent to each other every other one in the circumferential direction, The fluid device according to claim 4.

6. The arrangement of the outer radial groove flow passages and the inner radial groove flow passages is repeated for each set of two or four of the through-flow passages adjacent in the circumferential direction. The fluid device of claim 5 .

7. the inner circumferential connecting groove flow passage, the plurality of through-flow passages that are aligned in the circumferential direction and open on the end face, and the outer circumferential connecting groove flow passage are each arranged on a concentric circle on the end face. The fluid device according to any one of claims 4 to 6.

8. The second housing is a swing housing portion having an axis; internal teeth provided on an inner peripheral surface of the swing housing portion; a carrier supported by the swing housing portion so as to be rotatable about the axis line via two bearings provided spaced apart from each other along the axis line of the swing housing portion; a crankshaft supported by the carrier so as to be rotatable about another axis parallel to the axis; an oscillating gear that is regulated to oscillating rotation by the crankshaft and meshes with the internal teeth; a supply / discharge plate having a plurality of supply / discharge flow paths that supply the working fluid between the inner peripheral surface of the oscillating housing portion and the oscillating gear and discharge the working fluid from between the inner peripheral surface of the oscillating housing portion and the oscillating gear; Equipped with the supply / discharge plate is disposed on the first housing side in a direction along the axis of the oscillating gear, and the plurality of supply / discharge flow paths each communicate with the second flow path; The fluid device according to any one of claims 4 to 7.

9. the inner peripheral connecting groove flow passage and the outer peripheral connecting groove flow passage formed on the end surface of the distribution plate supply and discharge working fluids of different pressures, or supply and discharge working fluids of the same pressure; The fluidic device of claim 8 .

10. a first housing having a first flow path; a second housing having more second flow paths than the first flow paths; a distribution plate that is sandwiched in a thickness direction with end surfaces thereof in contact with the first housing and the second housing, and has a third flow path that connects a predetermined one of the first flow paths and the second flow path; and The second housing is a swing housing portion having an axis; internal teeth provided on an inner peripheral surface of the swing housing portion; a carrier supported by the swing housing portion so as to be rotatable about the axis line via two bearings provided spaced apart from each other along the axis line of the swing housing portion; a crankshaft supported by the carrier so as to be rotatable about another axis parallel to the axis; an oscillating gear that is regulated to oscillating rotation by the crankshaft and meshes with the internal teeth; a supply / discharge plate having a plurality of supply / discharge flow paths that supply the working fluid between the inner peripheral surface of the oscillating housing portion and the oscillating gear and discharge the working fluid from between the inner peripheral surface of the oscillating housing portion and the oscillating gear; Equipped with the supply / discharge plate is disposed on the first housing side in a direction along the axis of the oscillating gear, the supply / discharge flow paths communicate with the second flow path, and The third flow path in the distribution plate is a plurality of through-flow passages arranged side by side in a circumferential direction and opening on the end surface; a connecting groove flow path formed on each of the end faces, which are the front and rear surfaces of the distribution plate, and formed in a circumferential direction along the end faces to connect the plurality of through-flow passages; and a peripheral connecting groove flow path formed on the end faces along the circumferential direction to connect the plurality of through-flow passages radially outward of the plurality of through-flow passages; the connecting groove flow passage is an inner circumferential connecting groove flow passage formed in the end surface along a circumferential direction and connecting the plurality of through-flow passages radially inward of the plurality of through-flow passages; an outer radial groove formed on the end surface along a radial direction and connecting the through-flow passage and the outer circumferential connecting groove, the through-flow passage opening on the end surface; an inner radial groove flow path formed in the end surface along a radial direction and connecting the through flow path opening at the end surface and the inner circumferential connecting groove flow path; and the outer radial groove passages and the inner radial groove passages are respectively connected to the through-passages adjacent to each other in the circumferential direction, or the outer radial groove passages and the inner radial groove passages are respectively connected to the through-passages that are alternately adjacent to each other in the circumferential direction, and the arrangement of the outer radial groove passages and the inner radial groove passages is repeated for every four of the through-passages that are adjacent to each other in the circumferential direction. Fluid equipment.

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