Fluidic device

Abstract

The present application relates to a fluid device. The fluid device (1) of the present application includes a first housing (45) having first flow paths (111-114), a second housing (2, 3, 35) having second flow paths (41, 42) in a number greater than that of the first flow paths, and a distribution plate (100) having third flow paths (103-107) connecting predetermined first flow paths and second flow paths. The distribution plate is sandwiched between the first housing and the second housing in a thickness direction of the distribution plate in a state in which end surfaces (101, 102) of the distribution plate are in contact with the first housing and the second housing, respectively. The third flow paths include a plurality of through flow paths (103) arranged in a circumferential direction and opened at the end surfaces, and a link groove flow path (104, 105) formed in the circumferential direction and linking the plurality of through flow paths.

Description

Technical Field

[0001] This invention relates to fluid apparatus. Background Technology

[0002] Hydraulic pumps and hydraulic motors, such as those described in Patent Document 1, are known. Patent Document 1 discloses an oil passage for allowing working oil to flow to different positions in the circumferential direction relative to the main shaft. Furthermore, it discloses a structure in which a restraining member 130 serves as the oil passage for supplying working oil.

[0003] The constraint member 130 has: a groove formed concavely on the outer peripheral surface of the constraint member 130; and a through hole disposed radially inward from the groove and extending axially. The groove and the through hole are selectively connected to each other. Moreover, the constraint member 130 is thermofitted with a cylindrical recess 186 that surrounds the constraint member 130 radially outward throughout its entire circumference.

[0004] Existing technical documents

[0005] Patent documents

[0006] Patent Document 1: Japanese Patent Application Publication No. 2002-202069 Summary of the Invention

[0007] The problem the invention aims to solve

[0008] However, in the conventional structure described in Patent Document 1, the oil passage is formed between the outer peripheral surface of the restraining member 130 and the inner peripheral surface of the cylindrical recess 186. Therefore, multiple grooves are formed axially on the outer peripheral surface of the restraining member 130. Consequently, it is difficult to reduce the axial dimension of the restraining member 130 in order to supply and discharge working oil to drive the fluid device. Therefore, there is a problem that it is difficult to make the fluid device thinner.

[0009] The present invention provides a fluid device that can be miniaturized and space-saving with a simple construction.

[0010] Solution for solving the problem

[0011] (1) A fluid device according to one embodiment of the present invention comprises: a first housing having a first flow path; a second housing having a greater number of second flow paths than the number of first flow paths; and a distribution plate having a third flow path connecting predetermined first flow paths to the second flow paths. The distribution plate is sandwiched between the first housing and the second housing in the thickness direction with its end faces in contact with the first housing and the second housing respectively. The third flow path comprises: a plurality of through flow paths arranged circumferentially and opening at the end faces; and a connecting groove flow path formed circumferentially and connecting the plurality of through flow paths.

[0012] According to a fluid device based on a technical solution of the present invention, a first flow path and a second flow path can be connected by a distribution plate having a connecting groove flow path formed as a groove on its end face, thereby distributing fluid to the second flow path, which has a greater number than the first flow paths. Thus, fluid can be distributed between the first and second flow paths in the direction from the first housing to the second housing using only the thickness of the distribution plate. Consequently, compared to the prior art, the size of the device structure in the direction from the first housing to the second housing can be reduced.

[0013] (2) Alternatively, the connecting groove flow path may be formed on the end face of the distribution plate.

[0014] (3) Alternatively, multiple through-flow paths may be arranged on the end face at equal intervals in the circumferential direction.

[0015] (4) Alternatively, the connecting groove flow path may have: an outer peripheral connecting groove flow path, which is arranged at a position radially outward compared to the plurality of through flow paths, connecting the plurality of through flow paths; and an inner peripheral connecting groove flow path, which is arranged at a position radially inward compared to the plurality of through flow paths, connecting the plurality of through flow paths.

[0016] (5) Alternatively, the third flow path may further include: an outer diameter direction groove flow path formed radially on the end face, connecting the through flow path and the outer peripheral connecting groove flow path radially; and an inner diameter direction groove flow path formed radially on the end face, connecting the through flow path and the inner peripheral connecting groove flow path radially. Alternatively, the outer diameter direction groove flow path and the inner diameter direction groove flow path may be connected to the through flow paths adjacent to each other in the circumferential direction, or connected to the through flow paths adjacent to each other in the circumferential direction with one through flow path in between.

[0017] (6) Alternatively, the outer diameter direction groove flow path and the inner diameter direction groove flow path may be configured to repeat in groups of two or four adjacent through flow paths in the circumferential direction.

[0018] (7) Alternatively, the inner circumferential connecting groove flow path, the plurality of through flow paths, and the outer circumferential connecting groove flow path are respectively arranged on concentric circles on the end face.

[0019] (8) Alternatively, the second housing may include: a swing housing portion having an axis; an internal gear disposed on the inner circumferential surface of the swing housing portion; a gear carrier supported on the swing housing portion by means of two bearings disposed separately from each other along the axis of the swing housing portion in a manner rotatable about the axis; a crankshaft supported on the gear carrier in a manner rotatable about another axis parallel to the axis; a swing gear whose rotational motion is restricted to swing rotation by the crankshaft and meshes with the internal gear; and a supply and discharge plate having a plurality of supply and discharge flow paths for supplying working fluid between the inner circumferential surface of the swing housing portion and the swing gear and for discharging working fluid from the inner circumferential surface of the swing housing portion and the swing gear. Alternatively, the supply and discharge plate may be disposed on the first housing side of the swing gear in the direction along the axis, and the plurality of supply and discharge flow paths may communicate with the second flow path respectively.

[0020] (9) Alternatively, the inner circumferential connecting groove flow path and the outer circumferential connecting groove flow path can supply and discharge working fluids at different pressures, or supply and discharge working fluids at the same pressure.

[0021] (10) Another fluid device according to the present invention comprises: a first housing having a first flow path; a second housing having a greater number of second flow paths than the number of first flow paths; and a distribution plate having a third flow path connecting a predetermined first flow path to a second flow path. The distribution plate is sandwiched between the first housing and the second housing in the thickness direction of the distribution plate, with its end faces in contact with the first housing and the second housing respectively. The second housing includes: a swing housing portion having an axis; an internal gear disposed on the inner circumferential surface of the swing housing portion; a gear carrier supported on the swing housing portion by means of two bearings disposed separately from each other along the axis of the swing housing portion, so as to be rotatable about the axis; a crankshaft supported on the gear carrier so as to be rotatable about another axis parallel to the axis; a swing gear whose rotational motion is restricted to swing rotation by the crankshaft and meshes with the internal gear; and a supply and discharge plate having a plurality of supply and discharge flow paths for supplying working fluid between the inner circumferential surface of the swing housing portion and the swing gear and for discharging working fluid from the inner circumferential surface of the swing housing portion and the swing gear. The supply and discharge plate is disposed on the first housing side of the swing gear in the direction along the axis, and the plurality of supply and discharge flow paths communicate with the second flow path. The third flow path includes: a plurality of through flow paths arranged circumferentially and opening on the end face; an outer peripheral connecting groove flow path, which serves as a connecting groove flow path connecting the plurality of through flow paths, formed circumferentially on the end face and connecting the plurality of through flow paths at a position radially outward of the plurality of through flow paths; an inner peripheral connecting groove flow path, which serves as the connecting groove flow path, formed circumferentially on the end face and connecting the plurality of through flow paths at a position radially inward of the plurality of through flow paths; an outer diameter direction groove flow path formed radially on the end face and radially connecting the through flow paths and the outer peripheral connecting groove flow path; and an inner diameter direction groove flow path formed radially on the end face and radially connecting the through flow paths and the inner peripheral connecting groove flow path. The outer diameter direction groove flow path and the inner diameter direction groove flow path are respectively connected to the through flow paths that are adjacent to each other in the circumferential direction, or the outer diameter direction groove flow path and the inner diameter direction groove flow path are respectively connected to the through flow paths that are adjacent to each other in the circumferential direction with one through flow path in between. The configuration of the outer diameter direction groove flow path and the inner diameter direction groove flow path is repeated in groups of four through flow paths that are adjacent to each other in the circumferential direction.

[0022] With this configuration, the first and second flow paths can be connected using a distribution plate with grooves formed on its end face, allowing fluid to be split and merged between the first and second flow paths, which are more numerous than the first flow paths. Thus, fluid can be distributed between the first and second flow paths in the direction from the first housing to the second housing using only the thickness of the distribution plate. Consequently, compared to the prior art, the size of the device structure in the direction from the first housing to the second housing can be reduced.

[0023] Therefore, it is unnecessary to form multiple concave grooves on the outer periphery of the constraint member in the axial direction, as in the structure of Patent Document 1. Thus, the axial dimension can be reduced while allowing the fluid device to be driven by the supply and discharge of working oil. In other words, the fluid device can be made thinner.

[0024] Therefore, the possibility of working oil leakage due to gaps between the constraint member that forms the flow path (oil passage) and the cylindrical recess, as in the structure of Patent Document 1, can be eliminated, thus improving sealing performance. Furthermore, by using the first and second outer shells to clamp and secure the plate-shaped distribution plate, the distribution plate can be pressed down using fastening members or the like. Therefore, airtightness can be ensured and sealing performance can be reliably improved.

[0025] Furthermore, the distribution plate can be manufactured simply by forming a groove on the end face as a third flow path. Therefore, it can be manufactured by machining or casting, reducing the number of manufacturing steps and shortening operation time. Moreover, the required airtightness can be maintained simply by forming a flat surface on the end face of the distribution plate, thus avoiding the need for excessive machining precision. Therefore, it is possible to achieve both the required airtightness and ease of manufacturing.

[0026] The effects of the invention

[0027] According to the present invention, a fluid device can be provided that can be miniaturized and space-saving with a simple structure, can maintain the sealing of the working oil, and can prevent the leakage of the working oil, thereby improving the operating efficiency. Attached Figure Description

[0028] Figure 1 This is a side view (partial cross-sectional view) of the hydraulic motor in an embodiment of the present invention.

[0029] Figure 2 It is along Figure 1 A sectional view along line II-II.

[0030] Figure 3 yes Figure 1 An enlarged view of part III.

[0031] Figure 4 yes Figure 1An enlarged view of the portion shown in VI.

[0032] Figure 5 It is along Figure 1 The diagram shows a cross-sectional view along the VV line and is a diagram illustrating the flow path of the hydraulic motor in an embodiment of the present invention.

[0033] Figure 6 It is along Figure 1 The diagram shows a cross-sectional view along line VI-VI and is a diagram illustrating the flow path of the distribution plate in an embodiment of the present invention.

[0034] Figure 7 It is along Figure 1 The diagram shows a cross-sectional view along line VII-VII and is a diagram illustrating the flow path of the distribution plate in an embodiment of the present invention.

[0035] Figure 8 This is a cross-sectional view showing the distribution plate in an embodiment of the present invention.

[0036] Figure 9 It is along Figure 1 The diagram shows a cross-sectional view along line IX-IX and is a diagram illustrating the flow path of the hydraulic motor in an embodiment of the present invention.

[0037] Figure 10 It is along Figure 1 The diagram shows a cross-sectional view along line XX and is a diagram illustrating the flow path of the hydraulic motor in an embodiment of the present invention.

[0038] Figure 11 This is a cross-sectional view showing the flow path of the hydraulic motor in an embodiment of the present invention.

[0039] Figure 12 This represents another pressure state in an embodiment of the present invention. Figure 7 The corresponding sectional view.

[0040] Explanation of reference numerals in the attached figures

[0041] 1. Hydraulic motor (fluid device); 2. Swing housing (second housing); 3. Rotating part (second housing); 4. Crankshaft (eccentric rotating body); 5. Swing gear; 6. Gear carrier (rotating component); 7. First swing housing; 8. Second swing housing; 12, 13. Bearings; 31. First gear carrier (gear carrier); 32. Second gear carrier (gear carrier); 33. Base plate (second housing); 35. Circular plate (second housing); 35a. First end; 41. Supply path (second flow path); 41a. Supply opening; 42. Discharge path (second flow path); 42a. Discharge opening; 45. Oil distribution part (first housing); 45a. End face; 46. Supply and discharge plate (port plate) ; 46a, Through hole (supply / discharge 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, Working chamber; 90, Internal toothed pin; 100, Distribution plate; 101, 102, End face; 103-107, Third flow path; 103, Through flow path; 104, Outer peripheral connecting groove flow path (connecting groove flow path); 105, Inner peripheral connecting groove flow path (connecting groove flow path); 106, Outer diameter direction groove flow path (connecting groove flow path); 107, Inner diameter direction groove flow path (connecting groove flow path); 111-114, First flow path; C1, First axis (axis); P1-P4, Pressure. Detailed Implementation

[0042] Hereinafter, a first embodiment of the fluid device of the present invention will be described based on the accompanying drawings.

[0043] Figure 1 This is a side view (partial cross-section) showing a hydraulic motor as an example of a fluid device in this embodiment. Figure 2 It is along Figure 1 A sectional view along line II-II. Figure 3 yes Figure 1 An enlarged view of part III. Figure 4 yes Figure 1 An enlarged view of the portion shown in IV. Figure 5 It is along Figure 1 A cross-sectional view of the VV line. Figure 6 It is along Figure 1 A sectional view along line VI-VI. Figure 7 It is along Figure 1 A sectional view along line VII-VII. Figure 8 This is a cross-sectional view of the distribution plate. Figure 9 It is along Figure 1 A cross-sectional view of the IX-IX line. Figure 10 It is along Figure 1 A cross-sectional view along the XX line. Figure 11This is a cross-sectional view showing the flow path of a hydraulic motor. In the accompanying drawings, reference numeral 1 indicates a hydraulic motor.

[0044] As a fluid device in this embodiment, a hydraulic motor will be used as an example for description. However, it is not limited to this case; for example, a hydraulic pump structure can also be used as a fluid device.

[0045] <Hydraulic Motor>

[0046] like Figures 1-4 As shown, the hydraulic motor 1 has: a cylindrical swing housing 2; and a rotating part 3, which is rotatably supported on the inner circumferential surface of the swing housing 2 by means of two bearings 12, 13 (first bearing 12, second bearing 13).

[0047] Bearings 12 and 13 are angular contact ball bearings. However, they are not limited to this; various other ball bearings, such as deep groove ball bearings and sliding bearings, can be used as bearings 12 and 13.

[0048] The central axis of the swing housing 2 is aligned with the rotation axis of the rotating part 3. In the following description, these central axes and rotation axes are collectively referred to as the first axis (an example of an axis) C1.

[0049] Furthermore, in the following description, the direction parallel to the first axis C1 is sometimes simply referred to as the axial direction, the rotation direction of the rotating part 3 is referred to as the circumferential direction, and the radial direction of the rotating part 3 is sometimes simply referred to as the radial direction.

[0050] <Swinging outer casing>

[0051] like Figures 1-4 As shown, the swing housing 2 includes a first swing housing 7 and a second swing housing 8 that are divided in the axial direction.

[0052] The first swing housing 7 is disposed on the first direction side in the axial direction. Figure 1 (Left side of the middle). The second swing housing 8 is disposed on the second direction side, which is opposite to the first direction in the axial direction ( Figure 1 (The right side of the middle). In addition, the swing housing part 2 does not necessarily have to be divided in the axial direction, and can also be a structure that is not divided in the axial direction.

[0053] The first swing housing 7 is cylindrical. On the outer peripheral surface 7a of the first swing housing 7, near the first end 7b located in the first direction, a radially outwardly projecting flange 9 is formed. The flange 9 is used to mount the hydraulic motor 1 to an external device (not shown). A through hole 9a (not shown) is formed in the flange 9 in the thickness direction (axial direction) for a bolt (not shown) to pass through.

[0054] The portion of the peripheral wall 7e of the first swing housing 7, extending from the second end 7d on the second direction side to the axial center, is a thick-walled portion 10 with a wall thickness greater than that of other portions. The second end 10c of the thick-walled portion 10 on the second direction side is located on the same plane as the second end 7d of the first swing housing 7. That is, the second end 10c of the thick-walled portion 10 constitutes a part of the second end 7d of the first swing housing 7.

[0055] A plurality of pin grooves 10a (for example, 13 in this embodiment) are formed on the inner circumferential surface 10d of the thick-walled portion 10. Each pin groove 10a is formed along the axial direction on the entire thick-walled portion 10 and is arranged at equal intervals in the circumferential direction. The pin grooves 10a are semi-circular when viewed from the axial direction.

[0056] Cylindrical internal toothed pins (an example of internal teeth) 90 are rotatably housed in each pin groove 10a. The pin groove 10a is semi-circular when viewed axially; therefore, the internal toothed pin 90 has a shape that protrudes radially inward from the inner circumferential surface 10d of the thick-walled portion 10 by a semi-circular amount. The internal toothed pin 90 functions as internal teeth that mesh with the oscillating gear 5 described later.

[0057] A first through hole 19 extending axially is formed on the outer periphery of the thick-walled portion 10. The first through holes 19 are disposed between each pin groove 10a and are equally spaced in the circumferential direction. The number of first through holes 19 is, for example, eight. The shank 20a of the bolt (an example of a fixing part and a threaded part) 20 is inserted into these first through holes 19. The first swing housing 7, the second swing housing 8, and the feed plate 46 described later are fastened together by the bolts 20 and integrated.

[0058] On the inner circumferential surface 7c of the first swing housing 7, a first bearing housing portion 11 with a larger inner diameter is formed by means of a step portion 11a at a position closer to the first direction than the thick-walled portion 10. The outer ring 12a of the first bearing 12 is fitted into the first bearing housing portion 11. The positioning between the first bearing 12 and the first swing housing 7 is achieved by the outer ring 12a abutting against the step portion 11a.

[0059] On the inner circumferential surface 7c of the first swing housing 7, a sealing element housing 14 with a larger inner diameter is formed by means of a stepped portion 14a at a position closer to the first bearing housing 11 in the first direction. A portion of a sealing portion 15 is fitted into the sealing element housing 14. The sealing portion 15 seals the first swing housing 7 and the rotating portion 3.

[0060] As the sealing part 15, a floating seal is used, for example. However, the sealing part 15 is not limited to this case, and various kinds of sealing parts such as gaskets and mechanical seals can be used.

[0061] A first gear carrier side first labyrinth portion 16 is formed at the first end 7b of the first swing housing 7, the inner diameter of which is larger than the inner diameter of the sealing housing portion 14.

[0062] The first labyrinth section 16 on the first gear carrier side cooperates with the rotating section 3 to form the first labyrinth 38. Due to the first labyrinth 38, dust and the like are difficult to penetrate from the outside between the first swinging outer shell 7 and the rotating section 3.

[0063] The second end 7d of the first swing housing 7 corresponds to the dividing surface between the first swing housing 7 and the second swing housing 8. The outer periphery of the second end 7d of the first swing housing 7 is formed entirely flat. An annular O-ring groove 17 is formed at 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 installed in the O-ring groove 17. The O-ring 18 ensures the sealing between the first swing housing 7 and the second swing housing 8.

[0064] The second swing housing 8 is formed in an annular shape. On the peripheral wall 8a of the second swing housing 8, a second through hole 22 is formed at a position corresponding to the first through hole 19 of the first swing housing 7, which communicates with the first through hole 19.

[0065] The second through hole 22 is formed with the same diameter as the first through hole 19 and is located on the same axis as the first through hole 19. A countersunk portion 23 is formed on most of the second through hole 22 in the second direction. The head 20b of the bolt 20 is inserted into the countersunk portion 23.

[0066] The first end 8b of the second swing housing 8, located on the first direction side, corresponds to the dividing surface between the first swing housing 7 and the second swing housing 8. A pressure plate 21 is integrally formed on the first end 8b of the second swing housing 8, protruding radially inward from the inner circumferential surface 8c of the second swing housing 8.

[0067] The pressure plate 21 is formed in an annular shape when viewed axially. The pressure plate 21 seals, from the second direction side, the working chambers 66a, 66b, and 66c formed between the inner circumferential surface 7c of the first swing housing 7 and the outer circumferential surface of the swing gear 5 (described later). Figure 11 ).

[0068] Furthermore, when the first swing housing 7 and the second swing housing 8 are integrally formed, the pressure plate 21 can be formed, for example, in a manner that separates it from the swing housing portion 2.

[0069] On the inner circumferential surface 21a of the pressure plate 21, a first labyrinth portion 25 on the second gear carrier side is formed on most of the portion except for the end located on the first direction side. The first labyrinth portion 25 on the second gear carrier side is formed with the step portion 25a in such a way that its inner diameter is larger than the inner diameter of the inner circumferential surface 21a of the pressure plate 21.

[0070] The first labyrinth section 25 on the second gear carrier side cooperates with the rotating section 3 to form the second labyrinth 40. Due to the second labyrinth 40, it is difficult for working oil to leak from between the second swing housing 8 and the rotating section 3 (details will be discussed later).

[0071] On the inner circumferential surface 8c of the second swing housing 8, a second bearing housing 24 with a larger inner diameter formed by means of a step portion 24a is formed at a position closer to the second direction than the pressure plate 21. The outer ring 13a of the second bearing 13 is fitted into the second bearing housing 24. The positioning between the second bearing 13 and the second swing housing 8 is achieved by the abutting between the outer ring 13a and the step portion 24a.

[0072] An O-ring groove 26, which is annular in axial view, is formed at the second end 8d on the second direction side of the second swing housing 8. An O-ring 27 is installed in the O-ring groove 26. The O-ring 27 ensures the seal between the second swing housing 8 and the cover 29 described later.

[0073] At the second end 8d of the second swing housing 8, a plurality of internal threads 28 are formed at equal intervals in the circumferential direction at a position radially inward compared to the O-ring groove 26. These internal threads 28 are used to fix the cover 29 to the second swing housing 8.

[0074] <Mask>

[0075] Cover 29 blocks the opening 8e of the second swing housing 8 from the second direction side. Cover 29 is formed, for example, by stamping a metal sheet in such a way that most of the central part bulges out toward the second direction side.

[0076] The outer periphery of the cover 29 is provided as an outer flange 29a. The outer flange 29a overlaps with the second end portion 8d of the second swing housing 8.

[0077] A through hole 29b extending through the thickness of the cover 29 is formed in the outer flange portion 29a. The through hole 29b is formed at a position corresponding to the internal thread portion 28 of the second swing housing 8. A bolt 30 is inserted into the through hole 29b from the second direction side.

[0078] The cover 29 is fixed to the second swing housing 8 by fastening the bolt 30 to the internal thread 28 of the second swing housing 8.

[0079] <Supply and Arrangement Board>

[0080] The supply and discharge plate (port plate) 46 is secured by bolts 20 inserted into the second through hole 22 of the second swing housing 8 and the first through hole 19 of the first swing housing 7. The supply and discharge plate 46 is disposed at the first end 10b on one side of the thick-walled portion 10. The supply and discharge plate 46 is a plate for supplying working oil to or discharging working oil from the working chambers 66a, 66b, and 66c, which will be described later.

[0081] The feed plate 46 is formed in an annular shape when viewed from the axial direction. The outer diameter of the feed plate 46 is the same as or slightly smaller than the diameter of the inner circumferential surface 7c of the first swing housing 7. Therefore, the feed plate 46 is fitted into the inner circumferential surface 7c of the first swing housing 7 and is disposed at the first end 10b of the thick-walled portion 10.

[0082] On the outer periphery of the feed plate 46, an internal thread 47 is formed at a position corresponding to the first through hole 19 of the first swing housing 7. Thus, after the bolt 20 is inserted from the second swing housing 8 side in the order of the second through hole 22 and the first through hole 19, it is tightened to the internal thread 47 of the feed plate 46. Therefore, the first swing housing 7, the second swing housing 8, and the feed plate 46 can be fastened together as a single unit using the bolts 20.

[0083] In the supply and discharge plate 46, a portion located radially inward of the internal thread portion 47 has a plurality of through holes (supply and discharge ports) 46a extending through in the thickness direction. Thus, working oil can be supplied to or discharged from the working chambers 66a, 66b, and 66c via the through holes 46a (details will be discussed later).

[0084] The number of through holes (supply / discharge ports) 46a corresponds to the number of pin slots 10a formed in the first swing housing 7. For example, in this embodiment, the number of through holes 46a is 13. Each through hole (supply / discharge port) 46a is formed such that the opening on the side of the thick-walled portion 10 is located at the center between each adjacent pin slot 10a in the circumferential direction, and is located radially inward than the inner circumferential surface 10d of the thick-walled portion 10.

[0085] On the inner circumferential surface 46b of the feed plate 46, a plate-side labyrinth portion 48 is formed on most of the portion except for the end located in the second direction. The plate-side labyrinth portion 48 is formed by means of a step portion 48a such that its inner diameter is larger than the inner diameter of the inner circumferential surface 46b of the feed plate 46.

[0086] The labyrinth section 48 on the side of the plate cooperates with the rotating section 3 to form the third labyrinth 49. Due to the third labyrinth 49, it is difficult for working oil to leak from between the supply plate 46 and the rotating section 3 (details will be discussed later).

[0087] <Rotating Part>

[0088] The main structure of the rotating part 3, which is held in the swing housing part 2 in a rotatable manner, is as follows: a gear carrier part (rotating member) 6, which is supported on both sides in the axial direction by means of bearings 12 and 13 to be rotatable; a plurality of (for example, three in this embodiment) crankshafts 4, which are rotatably supported on the gear carrier part 6; and a swing gear 5, which is rotatably supported on the crankshafts 4.

[0089] The gear carrier portion 6 includes a first gear carrier 31 and a second gear carrier 32, which are divided axially. The first gear carrier 31 is disposed on the first direction side. The second gear carrier 32 is disposed on the second direction side.

[0090] The first gear carrier 31 includes: a circular plate-shaped base plate portion 33; and a plurality of (for example, three in this embodiment) support portions 34, which protrude from a second end portion 33b located on the second direction side of the base plate portion 33 toward the second direction.

[0091] Furthermore, the first gear carrier 31 is formed integrally with the base plate portion 33 and the support portion 34.

[0092] The outer peripheral surface 33c of the substrate portion 33 gradually increases in diameter from the second end portion 33b toward the first end portion 33a located in the first direction by means of the stepped portion.

[0093] Specifically, the outer peripheral surface 33c of the substrate portion 33 has a first outer peripheral surface 33d, a second outer peripheral surface 33e, a third outer peripheral surface 33f, and a fourth outer peripheral surface 33g sequentially from the second end portion 33b side.

[0094] The second outer peripheral surface 33e is formed on the first outer peripheral surface 33d by means of a large step portion 33h, and the outer diameter of the second outer peripheral surface 33e is larger than the outer diameter of the first outer peripheral surface 33d. The third outer peripheral surface 33f is formed on the second outer peripheral surface 33e by means of a small step portion 33i, and the outer diameter of the third outer peripheral surface 33f is larger than the outer diameter of the second outer peripheral surface 33e. The fourth outer peripheral surface 33g is formed on the third outer peripheral surface 33f by means of a middle step portion 33j, and the outer diameter of the fourth outer peripheral surface 33g is larger than the outer diameter of the third outer peripheral surface 33f.

[0095] The portion of the first gear carrier 31 having the first outer peripheral surface 33d is inserted into the plate-side labyrinth portion 48 of the feed 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 33b of the first gear carrier 31 is located on the second direction side, which is closer to the step portion 48a of the feed plate 46.

[0096] Thus, the third maze 49 is composed of the first outer peripheral surface 33d of the first gear carrier 31, the second end 33b, and the plate-side maze portion 48 of the supply plate 46.

[0097] The inner ring 12b of the first bearing 12 is fitted into the third outer peripheral surface 33f. The first bearing 12 and the first gear carrier 31 are positioned by the inner ring 12b abutting against the middle step portion 33j. Thus, the first gear carrier 31 is positioned relative to the first oscillating housing 7. Moreover, the first gear carrier 31 is rotatably supported on the first oscillating housing 7 by means of the first bearing 12.

[0098] The fourth outer peripheral surface 33g of the first gear carrier 31 is radially opposite to the sealing element receiving portion 14 of the first swing housing 7. Thus, a sealing portion 15 is disposed between the fourth outer peripheral surface 33g of the first gear carrier 31 and the sealing element receiving portion 14 of the first swing housing 7.

[0099] A circular plate portion 35, which is circular in shape when viewed from the axial direction, is integrally formed at the end of the fourth outer peripheral surface 33g located on the first direction side.

[0100] The second end portion 35b of the circular plate portion 35, located on the second direction side, is axially opposite to the first end portion 7b of the first swing housing 7. The outer diameter of the circular plate portion 35 is equal to the diameter of the outer peripheral surface 7a of the first swing housing 7.

[0101] A sealing member receiving recess 36, which is annular in axial view, is formed at the second end 35b of the circular plate portion 35. The sealing member receiving recess 36 is smoothly connected to the fourth outer peripheral surface 33g. A portion of the sealing portion 15 is received in the sealing member receiving recess 36. As a result, a seal is formed between the first swing housing 7 and the first gear carrier 31 (rotating portion 3).

[0102] At the outer periphery of the second end 35b of the circular plate portion 35, a second labyrinth portion 37 with a smaller outer diameter is formed on the first gear carrier side by means of a step. The first labyrinth 38 is composed of the second labyrinth portion 37 on the first gear carrier side and the first labyrinth portion 16 on the first gear carrier side formed in the first swing housing 7. The first labyrinth 38 is disposed on the radially outer side of the sealing portion 15, thereby reliably preventing the intrusion of dust and the like from the outside through the first swing housing 7 and the first gear carrier 31 (rotating portion 3).

[0103] An outer flange 39 protruding radially outward is formed on the outer peripheral surface 35c of the circular plate portion 35.

[0104] The outer flange portion 39 is used to mount the hydraulic motor 1 to an external device (not shown). A through hole 39a (not shown) is formed in the outer flange portion 39 in such a way that it extends through the thickness direction (axial direction) of the outer flange portion 39 for a bolt (not shown) to pass through.

[0105] A plurality of shaft support recesses 44 are formed at equal intervals in the circumferential direction at the second end portion 33b of the substrate portion 33. The plurality of shaft support recesses 44 are formed at a position near the outer periphery of the second end portion 33b (radially inward of the first outer peripheral surface 33d).

[0106] The shaft support recess 44 supports the crankshaft 4 for free rotation. A first bearing 59a for supporting the crankshaft 4 for free rotation is fitted into the shaft support recess 44. The first bearing 59a is, for example, a sliding bearing. However, it is not limited to this case as the first bearing 59a, and various types of bearings such as ball bearings can be used.

[0107] In the portion of the substrate 33 located radially inward from the second outer peripheral surface 33e, a plurality of supply paths 41, a plurality of discharge paths 42, and a liquid discharge passage (tank path) 43 are formed along the axial direction of the substrate 33.

[0108] Supply path 41 is an oil passage (flow path) for supplying working oil to a hydraulic pump (not shown). The end of supply path 41 located on the second direction side opens via a large step portion 33h. Thus, each supply path 41 has a supply opening portion 41a in the large step portion 33h.

[0109] Discharge path 42 is an oil passage (flow path) for discharging working oil from the hydraulic motor 1. The end of discharge path 42 located on the second direction side also opens via a large step portion 33h. Thus, each discharge path 42 has a discharge opening portion 42a in the large step portion 33h.

[0110] The number of supply paths 41 and the number of discharge paths 42 are different from the number of through holes 46a of the supply and 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 set to 12, which is one less than the number of through holes 46a of the supply and discharge plate 46.

[0111] Furthermore, the supply opening 41a of the supply path 41 and the discharge opening 42a of the discharge path 42 are alternately arranged on the same pitch circle in the circumferential direction. Each supply opening 41a and each discharge opening 42a are paired one by one and arranged at equal intervals in the circumferential direction.

[0112] Drainage passage 43 is a flow path used to return leaked working oil from the hydraulic motor 1 to a tank (not shown).

[0113] The ends (ends on the first direction side) of the supply path 41, discharge path 42, and drain passage 43 are connected to the oil distribution section 45 via a distribution plate 100 provided at the first end 33a of the base plate section 33. The distribution plate 100 has flow paths 103 to 107 that can distribute to multiple flow paths. The oil distribution section 45 has multiple flow paths 111 to 114, which will be described later. The distribution plate 100 contacts the first end 35a on the first direction side of the circular plate section 35.

[0114] Working oil from the hydraulic pump is supplied to flow path 103-107 via multiple flow paths 111-114. Furthermore, working oil from flow paths 111-114 can be supplied to supply path 41 via distributable flow paths 103-107.

[0115] Furthermore, the working oil discharged to the discharge path 42 flows back to the tank via the distributable flow paths 103-107 and 111-114, or flows back to the supply path 41 again. Alternatively, the working oil discharged to the drain passage 43 may also flow back to the tank via a distribution flow path not shown.

[0116] Furthermore, details regarding the function of the working fluid will be discussed later.

[0117] A gap is formed between the large step portion 33h of the first gear carrier 31 and the feed plate 46. A sliding plate (piston plate) 50 is disposed in this gap.

[0118] The sliding plate 50 is formed in an annular shape when viewed axially. The inner circumferential surface of the sliding plate 50 fits into the first outer circumferential surface 33d of the first gear carrier 31. The sliding plate 50 is configured to be non-rotatable relative to the first gear carrier 31 and to slide freely in the direction of axis C1. Furthermore, the thickness of the sliding plate 50 is smaller than the gap between the large step portion 33h and the feed plate 46.

[0119] The sliding plate 50 has a plurality of through holes (through ports) 50c formed in such a manner that they correspond to the supply opening 41a of the supply path 41 and the discharge opening 42a of the discharge path 42. The through holes 50c corresponding to the supply opening 41a are arranged on the same axis as the supply opening 41a. The through holes 50c corresponding to the discharge opening 42a are arranged on the same axis as the discharge opening 42a.

[0120] A cylindrical piston 51 is provided at each supply opening 41a and each discharge opening 42a.

[0121] The piston 51 is slidably disposed in the supply path 41 and the discharge path 42. The piston 51 is pressed against the sliding plate 50 by springs 51s disposed in the supply path 41 and the discharge path 42.

[0122] Furthermore, 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, under the action of the spring 51s, protrudes from the large step portion 33h and abuts against the sliding plate 50. As a result, the surface 50b of the sliding plate 50 located on the second direction side is pressed against the supply / discharge plate 46. Thus, each supply path 41 communicates with the through hole 50c of the sliding plate 50 via the piston 51.

[0123] Furthermore, each discharge path 42 is connected to the through hole 50c of the sliding plate 50 via the piston 51. Moreover, each through hole 50c of the sliding plate 50 is connected to the through hole 46a of the supply and discharge plate 46.

[0124] The support portion 34 of the first gear carrier 31 is formed as a column extending axially, and is triangular in shape when viewed axially. Each support portion 34 is arranged circumferentially between the shaft support recesses 44 of the base plate portion 33. Thus, each support portion 34 is arranged at equal intervals circumferentially on the second end portion 33b of the base plate portion 33. The pitch circle diameter of each support portion 34 is approximately the same as the pitch circle diameter of the shaft support recess 44.

[0125] The top end portion 34a of the support column 34 is formed flat. The top end portion 34a of the support column 34 and the second end portion 7d of the first swing housing 7 are located on the same plane. An internal thread portion 52 for a tight-fitting bolt is formed on the top end portion 34a of the support column 34.

[0126] The internal thread portion 52 includes: a fitting recess 52a, which is formed axially across a portion extending from the top end portion 34a of the support portion 34 to the axial center of the support portion 34; and an internal thread portion body 52b, which extends from the bottom of the fitting recess 52a toward a first direction. The first gear carrier 31 and the second gear carrier 32 are integrated by fastening a tight-fitting bolt (an example of another fixing portion) 53 relative to the internal thread portion 52.

[0127] The second gear carrier 32 is formed in the shape of a circular plate. The second gear carrier 32 is positioned such that its first end 32a on the first direction side abuts against the top end 34a of the support portion 34 constituting the first gear carrier 31. Therefore, a gap with the same height as the support portion 34 is formed between the base plate portion 33 of the first gear carrier 31 and the second gear carrier 32. The thick wall portion 10 of the first swing housing 7 surrounds this gap, thereby forming a swing gear housing portion for housing the swing gear 5.

[0128] The first end 32a of the second gear carrier 32 is formed flat overall. A through-hole 54 is formed in the second gear carrier 32 at the portion corresponding to the internal thread portion 52.

[0129] The fastening bolt 53 is inserted into the fitting hole 54 from the second direction side of the second gear carrier 32. Furthermore, by passing the fastening bolt 53 through the fitting recess 52a of the support portion 34 and fastening it to the internal threaded body 52b, the first gear carrier 31 and the second gear carrier 32 can be combined into one unit.

[0130] The fastening bolt 53 consists of a shank 53a, an external thread 53b, and a head 53c. The external thread 53b protrudes from the end of the shank 53a located in the first direction and is formed on the same axis as the shank 53a. The head 53c is formed at the end of the shank 53a located in the second direction.

[0131] With the fastening bolt 53 fastened to the internal thread portion 52 of the fastening bolt, the shank portion 53a of the fastening bolt 53 is fitted into the fitting recess 52a of the support portion 34 and the fitting hole 54 of the second gear carrier 32. Thus, the shank portion 53a of the fastening bolt 53 is arranged across the first gear carrier 31 and the second gear carrier 32.

[0132] A countersunk portion 55 connected to a fitting hole 54 is formed at the second end 32b on the second direction side of the second gear carrier 32. The head 53c of a fastening bolt 53 is inserted into the countersunk portion 55. This suppresses the protrusion height of the head 53c of the fastening bolt 53 from the second end 32b of the second gear carrier 32.

[0133] A reduced diameter portion 56 with a smaller outer diameter is provided on the outer peripheral surface 32c of the second gear carrier 32 via a stepped portion 56a. The inner ring 13b of the second bearing 13 is fitted into the reduced diameter portion 56. Thus, the second gear carrier 32 is rotatably supported on the second swing housing 8 by means of the second bearing 13.

[0134] A second labyrinth portion 57 on the second gear carrier side is formed in the reduced diameter portion 56, at a position closer to the first direction than the portion where the second bearing 13 is fitted. The outer diameter of the second labyrinth portion 57 on the second gear carrier side is smaller than the outer diameter of the reduced diameter portion 56 by means of the step portion 57a. The outer diameter of the second labyrinth portion 57 on the second gear carrier side is slightly smaller than the inner diameter of the first labyrinth portion 25 on the second gear carrier side of the second swing housing 8.

[0135] The top of the second labyrinth section 57 on the second gear carrier side is located on the second direction side, which is closer to the step section 25a of the first labyrinth section 25 on the second gear carrier side. The second labyrinth 40 is composed of the first labyrinth section 25 on the second gear carrier side of the second swing housing 8 and the second labyrinth section 57 on the second gear carrier side of the second gear carrier 32.

[0136] A plurality of shaft support holes 58 are formed at a position radially inward of the second labyrinth portion 57 on the second gear carrier side, spaced equally in the circumferential direction. For example, three in this embodiment.

[0137] The shaft support hole 58 supports the crankshaft (eccentric rotating body) 4 so that it can rotate freely. The shaft support hole 58 and the shaft support recess 44 of the first gear carrier 31 are located on the same shaft. The second bearing 59b is fitted into the shaft support hole 58.

[0138] The second bearing 59b is, for example, a sliding bearing. However, it is not limited to this case; various types of bearings, such as ball bearings, can be used as the second bearing 59b.

[0139] <crankshaft>

[0140] Each crankshaft 4 is rotatably supported in the shaft support recess 44 and the shaft support hole 58 by means of bearings 59a and 59b. Therefore, the crankshaft 4 can slide and rotate relative to the shaft support recess 44 and the shaft support hole 58 by means of bearings 59a and 59b.

[0141] In this embodiment, there are three crankshafts 4. Each crankshaft 4 has bearing portions 4a and 4b (first bearing portion 4a and second bearing portion 4b) and a cylindrical eccentric portion 4c.

[0142] Bearing portions 4a and 4b are rotatably supported by bearings 59a and 59b on the shaft support recess 44 and the shaft support hole 58. An eccentric portion 4c is disposed between bearing portions 4a and 4b and is integrally formed with bearing portions 4a and 4b.

[0143] The rotation axis of crankshaft 4 (second axis C2) is parallel to the first axis C1. Furthermore, the second axis C2 corresponds to the axis of bearing sections 4a and 4b.

[0144] The axial movement of crankshaft 4 is limited by thrust bearings 61a and 61b (first thrust bearing 61a and second thrust bearing 61b), first collar 70a and second collar 70b.

[0145] Thrust bearings 61a and 61b are positioned axially outward from bearing portions 4a and 4b. A first collar 70a is disposed in the shaft support recess 44 of the first gear carrier 31. A second collar 70b is disposed in the shaft support hole 58 of the second gear carrier 32.

[0146] The movement of the second thrust bearing 61b, which is located in the shaft support hole 58 of the second gear carrier 32, toward the second direction is limited by the retaining ring 62 located in the shaft support hole 58.

[0147] The axial length of the eccentric part 4c is formed within the axial width of the oscillating gear receiving part.

[0148] 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 swing housing 7. Therefore, the position of the end of the eccentric portion 4c located on the second direction side is approximately on the same plane as the position of the first end portion 8b of the second swing housing 8.

[0149] The axis of the eccentric portion 4c (the third axis C3) is eccentric relative to the second axis C2 of the crankshaft 4. The oscillating gear 5 is rotatably supported in the eccentric portion 4c by means of a third bearing 59c. The third bearing 59c is, for example, a sliding bearing. However, it is not limited to this case; various types of bearings, such as ball bearings, can be used as the third bearing 59c.

[0150] The outer diameter of the oscillating gear 5 is smaller than the diameter of the inner circumferential surface 10d of the thick-walled portion 10, so that it is housed in the oscillating gear housing. The axial thickness of the oscillating gear 5 is, for example, equal to the thickness of the eccentric portion 4c. Therefore, the position of the end of the oscillating gear 5 located on the second direction side is approximately on the same plane as the position of the first end 8b of the second oscillating housing 8.

[0151] Furthermore, a support hole 63 is formed in the oscillating gear 5 at a position corresponding to the crankshaft 4, through which the eccentric portion 4c of the crankshaft 4 passes.

[0152] The support holes 63 are arranged at equal intervals in the circumferential direction. A third bearing 59c is provided in each support hole 63. The axial movement of the oscillating gear 5 relative to the crankshaft 4 is limited by retaining rings 67 provided at both ends of the third bearing 59c. Thus, the rotational motion of the oscillating gear 5 is limited to oscillating rotation by the crankshaft 4.

[0153] In the oscillating gear 5, a clearance hole 64 is formed at a position corresponding to the support portion 34 of the first gear carrier 31, through which the support portion 34 passes. Furthermore, the shape of the clearance hole 64, when viewed from the axial direction, is set to a triangular shape in a manner corresponding to the shape of the support portion 34.

[0154] Furthermore, the size of the clearance hole 64 is formed to be sufficiently large compared to the outer surface shape of the support portion 34 to prevent the support portion 34 from obstructing the swing rotation of the swing gear 5.

[0155] The outer peripheral surface of the oscillating gear 5 is radially opposite to the inner toothed pin 90 of the first oscillating housing 7. External teeth 65 that mesh with the inner toothed pin 90 are formed on the outer peripheral surface of the oscillating gear 5. The number of teeth on the external teeth 65 is different from the number of teeth on the inner toothed pin 90.

[0156] For example, in this embodiment, the number of teeth on the external tooth 65 is 12, which is one less than the number of teeth on the internal tooth pin 90. This number is consistent with the number of supply paths 41 and discharge paths 42 formed in the first gear carrier 31.

[0157] During the oscillating rotation, any part of the oscillating gear 5 from the tooth tip 65a to the tooth root 65b is always in contact with the internal tooth pin 90. Thus, two working chambers 66a and 66b (first working chamber 66a and second working chamber 66b) are substantially formed between the inner circumferential surface 10d of the thick-walled portion 10 of the first oscillating housing 7 and the external tooth 65 of the oscillating gear 5. The two working chambers 66a and 66b are linearly symmetrical when viewed axially.

[0158] A working chamber 66c is formed between working chambers 66a and 66b. Working chambers 66a and 66b are distinguished according to the pressure state during operation. As will be described later, the position connected to the supply path 41 and under high pressure is designated as working chamber 66a, and the position connected to the discharge path 42 and under low pressure is designated as working chamber 66b. Therefore, the position under pressure that is not simultaneously connected to either the supply path 41 or the discharge path 42 is designated as working chamber 66c.

[0159] Multiple through holes 46a for supplying the plate 46 are connected to the working chambers 66a and 66b. Working oil can be supplied to or discharged from the working chambers 66a and 66b through the through holes 46a. This drives the hydraulic motor 1 to rotate.

[0160] <Distribution Board>

[0161] like Figure 1 , Figures 5-8 As shown, the distribution plate 100 is sandwiched between the oil distribution section 45 and the circular plate section 35 in the thickness direction. The distribution plate 100 is arranged with its end faces 101 and 102 in contact with the oil distribution section 45 and the circular plate section 35, respectively. The distribution plate 100 has a third flow path 103 to 107 that connects the first flow path 111 to 114 and the supply and discharge flow paths (second flow paths) 41 and 42.

[0162] The distribution plate 100 is sandwiched between the oil distribution section 45, which serves as the first outer shell, and the rotating section 3, which serves as the second outer shell and includes the circular plate section 35. The working oil (fluid) is split and merged between the first flow path 111-114 and the second flow path 41, 42 by using the third flow path 103-107.

[0163] The end face 101 of the distribution plate 100 located on the first direction side contacts the end face 45a of the oil distribution section 45. The end face 102 of the distribution plate 100 located on the second direction side contacts the first end portion 35a of the circular plate portion 35. As a result, the end faces 101 and 102 are pressed from the end face 45a and the first end portion 35a, thereby maintaining the distribution plate 100 in a sealed state.

[0164] Furthermore, by fastening the oil distribution section 45 and the circular plate section 35, the distribution plate 100 can also be pushed from both sides.

[0165] A plurality of through flow paths 103 are formed in the distribution plate 100 as a third flow path. The plurality of through flow paths 103 are formed to extend through the thickness direction of the distribution plate 100, and open at end faces 101 and 102 respectively. The plurality of through flow paths 103 are arranged circumferentially along the same circumference centered on axis C1 at end faces 101 and 102. The opening positions of the plurality of through flow paths 103 have equal spacing in the circumferential direction. The number of through flow paths 103 is equal to the total number of supply paths 41 and discharge paths 42. The number of through flow paths 103 corresponds to the number of pistons 51. In this embodiment, 24 through flow paths 103 are arranged circumferentially.

[0166] The openings at the end faces 101 of the multiple through flow paths 103 are arranged opposite to the first flow paths 111 to 114 which open at the end face 45a of the oil distribution section 45. Thus, the through flow paths 103 are connected to the first flow paths 111 to 114. Furthermore, it is not necessary for all through flow paths 103 to be opposite to the first flow paths 111 to 114 at the end face 101.

[0167] The openings at the end faces 102 of the plurality of through flow paths 103 are arranged opposite to the supply path 41 and the discharge path 42 that open at the first end 35a of the circular plate portion 35. Thus, the through flow paths 103 are connected to the supply path 41 and the discharge path 42. Furthermore, at the end faces 102, the through flow paths 103 are respectively opposite to the corresponding supply path 41 or discharge path 42.

[0168] Furthermore, the end face 101 of the distribution plate 100 is formed in a groove shape with an outer peripheral connecting groove flow path 104, an inner peripheral connecting groove flow path 105, an outer diameter direction groove flow path 106, and an inner diameter direction groove flow path 107 as a third flow path.

[0169] These peripheral connecting groove flow paths 104, inner peripheral connecting groove flow paths 105, outer diameter direction groove flow paths 106, and inner diameter direction groove flow paths 107 function as connecting groove flow paths that connect multiple through flow paths 103.

[0170] The outer peripheral connecting groove flow path 104 is formed in a ring shape along the circumference of the distribution plate 100, and is located radially outward from the plurality of through flow paths 103 that open at the end face 101. In addition, the outer peripheral connecting groove flow path 104 is formed with equal width and equal depth dimensions throughout the entire circumference.

[0171] The inner circumferential connecting groove flow path 105 is formed in a ring shape along the circumference of the distribution plate 100, and is located radially inward than the plurality of through flow paths 103 that open at the end face 101. Furthermore, the inner circumferential connecting groove flow path 105 is formed with equal width and equal depth dimensions throughout the entire circumference.

[0172] Furthermore, the outer peripheral connecting groove flow path 104 and the inner peripheral connecting groove flow path 105 are configured to have equal width and equal depth. The outer peripheral connecting groove flow path 104 and the inner peripheral connecting groove flow path 105 are arranged concentrically with axis C1 as the center.

[0173] The outer diameter direction groove flow path 106 is formed radially along the distribution plate 100 in such a way that it connects the through flow path 103 located at a predetermined position among the plurality of through flow paths 103 arranged in the circumferential direction and the outer peripheral connecting groove flow path 104. The inner diameter direction groove flow path 107 is formed radially along the distribution plate 100 in such a way that it connects the through flow path 103 located at a predetermined position among the plurality of through flow paths 103 arranged in the circumferential direction and the inner peripheral connecting groove flow path 105.

[0174] On the end face 102 of the distribution plate 100, similar to the end face 101, an outer peripheral connecting groove flow path 104, an inner peripheral connecting groove flow path 105, an outer diameter direction groove flow path 106, and an inner diameter direction groove flow path 107 are formed as connecting groove flow paths connecting multiple through flow paths 103. Furthermore, on the end faces 101 and 102, the outer peripheral connecting groove flow path 104 and the inner peripheral connecting groove flow path 105 are formed with substantially the same shape. Moreover, the outer peripheral connecting groove flow path 104 and the inner peripheral connecting groove flow path 105 are formed on the end faces 101 and 102 in a symmetrical arrangement in the thickness direction.

[0175] Furthermore, on end faces 101 and 102, the outer diameter direction groove flow path 106 and the inner diameter direction groove flow path 107 are formed with approximately the same shape. However, on end faces 101 and 102, the outer diameter direction groove flow path 106 and the inner diameter direction groove flow path 107 are formed in a different manner in circumferential configuration.

[0176] In this embodiment, on the end face 101, the outer peripheral connecting groove flow path 104 is connected to six through flow paths 103 via the outer diameter direction groove flow path 106. Furthermore, the inner peripheral connecting groove flow path 105 is connected to six through flow paths 103 via the inner diameter direction groove flow path 107.

[0177] Furthermore, on the end face 102, the outer peripheral connecting groove flow path 104 is connected to six through flow paths 103 via the outer diameter direction groove flow path 106. Moreover, the inner peripheral connecting groove flow path 105 is connected to six through flow paths 103 via the inner diameter direction groove flow path 107.

[0178] The outer peripheral connecting groove flow path 104 formed on the end face 101, the inner peripheral connecting groove flow path 105 formed on the end face 101, the outer peripheral connecting groove flow path 104 formed on the end face 102, the inner peripheral connecting groove flow path 105 formed on the end face 102, and the through flow path 103 connected to them form four independent flow paths that are separated from each other.

[0179] The four flow paths formed in the distribution plate 100 correspond to the four first flow paths 111 to 114 formed in the oil distribution section 45.

[0180] In addition, Figures 5-7 In the diagram, the correspondence between the four independent flow paths in the distribution board 100 and the four first flow paths 111 to 114 is indicated.

[0181] In addition, any one of the four independent flow paths, namely the inner diameter direction groove flow path 107 formed on the end face 101, the outer diameter direction groove flow path 106 formed on the end face 101, the inner diameter direction groove flow path 107 formed on the end face 102, and the outer diameter direction groove flow path 106 formed on the end face 102, is connected to the through flow path 103.

[0182] Furthermore, two or more of the following flow paths formed on the end face 101—the inner diameter direction groove flow path 107, the outer diameter direction groove flow path 106, the inner diameter direction groove flow path 107, and the outer diameter direction groove flow path 106—will not be formed in the same through flow path 103.

[0183] Thus, the four interconnected flow paths 103 that are open adjacently in the circumferentially arranged flow paths 103 are grouped together, and the outer diameter direction groove flow path 106 and inner diameter direction groove flow path 107 of the end face 101 and end face 102 are repeated in the circumferential direction. That is, the inner diameter direction groove flow path 107 formed on the end face 101, the outer diameter direction groove flow path 106 formed on the end face 101, the inner diameter direction groove flow path 107 formed on the end face 102, and the outer diameter direction groove flow path 106 formed on the end face 102 are grouped together and repeated in the circumferential direction.

[0184] Alternatively, the inner diameter direction groove flow path 107 formed on end face 101, the inner diameter direction groove flow path 107 formed on end face 102, the outer diameter direction groove flow path 106 formed on end face 101, and the outer diameter direction groove flow path 106 formed on end face 102 can be grouped together and repeated in the circumferential direction. Moreover, by reversing their circumferential direction, that is, the clockwise direction (or counterclockwise direction) when viewed from above, other repeating patterns can also be created.

[0185] The structure illustrated in this embodiment is as follows.

[0186] An inner diameter groove flow path 107 formed on the end face 102 is connected to flow path 111. An outer diameter groove flow path 106 formed on the end face 102 is connected to flow path 112. An inner diameter groove flow path 107 formed on the end face 101 is connected to flow path 113. An outer diameter groove flow path 106 formed on the end face 101 is connected to flow path 114.

[0187] In other words, when flow paths 111 to 114 are set to different pressure states, the pressure states of the four independent flow paths can correspond to the pressure states.

[0188] The opening at the end face 102 of the through flow path 103 connects to the supply path 41 and the discharge path 42 formed in the circular plate portion 35 and the base plate portion 33, which serve as the second housing. Of the four independent flow paths mentioned above, two are connected to the supply path 41, and the remaining two are connected to the discharge path 42. Furthermore, details regarding the function of the working oil will be discussed later. The operation of the hydraulic motor 1 will now be discussed in detail.

[0189] <Action of the hydraulic motor>

[0190] Next, the operation of hydraulic motor 1 will be explained.

[0191] In the hydraulic motor 1, working oil supplied by a hydraulic pump (not shown) is supplied to each supply path 41 via flow paths 111 and 113 of the oil distribution section 45 and the distribution plate 100.

[0192] Therefore, such as Figures 5-7 As shown, the working oil supplied by the hydraulic pump is transported through the flow path 111 and flows into the distribution plate 100 from the opening of the end face 45a of the oil distribution section 45. The working oil flowing into the distribution plate 100 flows through the through flow path 103 from the inner diameter direction groove flow path 107 formed on the end face 101 to the inner circumferential connecting groove flow path 105 formed on the end face 101.

[0193] In the distribution plate 100, working oil is diverted from the inner diameter direction groove flow path 107 connected to the inner circumferential connecting groove flow path 105 to other through flow paths 103. In the distribution plate 100 of this embodiment, working oil is distributed to five through flow paths 103. The distributed working oil further flows along the thickness direction of the distribution plate 100 in these through flow paths 103 and is supplied to each supply path 41 through the openings of the through flow paths 103 at the end faces 102.

[0194] Similarly, as Figures 5-7As shown, working oil supplied from the hydraulic pump is conveyed through flow path 113 and flows into the distribution plate 100 from the opening of the end face 45a of the oil distribution section 45. The working oil flowing into the distribution plate 100 flows into the through flow path 103 of the end face 101, and flows along the thickness direction of the distribution plate 100 in the through flow path 103. Furthermore, at the end face 102, the working oil flows into the inner circumferential connecting groove flow path 105 of the end face 102 via the inner diameter direction groove flow path 107.

[0195] In the distribution plate 100, working oil is diverted from the inner diameter direction groove flow path 107, which is connected to the inner circumferential connecting groove flow path 105, to other through flow paths 103. In this embodiment, the distribution plate 100 distributes the oil to five through flow paths 103. The distributed working oil is further supplied to each supply path 41 through the openings in the end face 102 of these through flow paths 103.

[0196] In multiple supply paths 41 and flow paths 111 and 113, the same pressure P1 is used to supply working oil. Furthermore, in... Figures 5-7 , Figure 11 In this context, the supplied working oil (fluid) is set to a high-pressure state, denoted by P1.

[0197] The working oil supplied to each supply path 41 is supplied to the working chambers 66a and 66b through the piston 51 of each supply opening 41a, the through hole 50c of the sliding plate 50, and the through hole 46a of the supply plate 46.

[0198] The piston 51 of each supply opening 41a slides relative to the sliding plate 50, which rotates integrally with the first gear carrier 31, under the condition that the spring 51s applies force toward the sliding plate 50. When the through hole 50c comes to a position aligned with the piston 51 due to the rotation of the sliding plate 50, the working oil supplied to the supply path 41 flows into the through hole 50c.

[0199] The sliding plate 50, which rotates integrally with the first gear carrier 31, slides relative to the supply plate 46, which is integral with the swing housing 2. When the through hole 46a reaches the position aligned with the through hole 50c due to the rotation of the sliding plate 50 and the supply plate 46, the working oil supplied to the through hole 50c flows into the through hole 46a.

[0200] Furthermore, when the through hole 46a and the through hole 50c are not connected, the through hole 46a is blocked by the sliding plate 50 to prevent working oil from leaking out or flowing back from the working chambers 66a and 66b through the through hole 46a.

[0201] The number of supply paths 41 (supply opening 41a and through hole 50c of sliding plate 50 communicating with supply opening 41a) is one less than the number of through holes 46a of supply plate 46. Furthermore, the number of discharge paths 42 (discharge opening 42a and through hole 50c of sliding plate 50 communicating with discharge opening 42a) is one less than the number of through holes 46a of supply plate 46.

[0202] Therefore, in either of the two chambers 66a and 66b, the supply path 41 is connected only through the through hole 46a of the supply plate 46. Moreover, in the other of the two chambers 66a and 66b, the discharge path 42 is connected only through the through hole 46a of the supply plate 46.

[0203] At this time, the through hole 46a of the supply and discharge plate 46 at the working chamber 66c is not connected to the through hole 50c of the sliding plate 50. Therefore, the supply path 41 and the discharge path 42 are not connected in the working chamber 66c.

[0204] Therefore, the internal pressure of either of the two studios 66a and 66b is higher than the internal pressure of either of the two studios 66a and 66b.

[0205] To make the explanation easier to understand, the following will refer to the two studios 66a and 66b, specifically studio 66a (… Figure 2 The pressure P1 on the left side of the chamber is greater than that in chamber 66b. Figure 2 The following explanation will focus on the case where the pressure P2 (on the right side of the diagram) is higher. Furthermore, in the following description, the chamber 66a with the higher pressure P1 will be referred to as the high-pressure chamber 66a. The chamber 66b with the lower pressure P2 than the high-pressure chamber 66a will be referred to as the low-pressure chamber 66b. The high-pressure chamber 66a is connected to the supply path 41. The low-pressure chamber 66b is connected to the discharge path 42.

[0206] In discharge path 42, the working oil flows at the same pressure P2. Furthermore, in Figures 5-7 , Figure 11 In this context, the discharged working oil (fluid) is set to a low-pressure state, denoted by P2.

[0207] By supplying working oil to the high-pressure chamber 66a, the oscillating gear 5 is pressed towards the low-pressure chamber 66b (see reference). Figure 2 (Y1 in the image). Working oil in the low-pressure chamber 66b is discharged via discharge path 42. As a result, on the low-pressure chamber 66b side, the internal toothed pin 90 meshes with the external toothed pin 65 of the oscillating gear 5. Thus, since the external toothed pin 90 has one less tooth than the internal toothed pin 90, the oscillating gear 5 is slightly deviated in the direction of rotation.

[0208] At this time, the gear carrier 6, in conjunction with the crankshaft 4, deviates in the rotational direction in relation to the oscillating gear 5. That is, the rotating part 3 rotates slightly relative to the oscillating housing part 2. Consequently, the sliding plate 50 rotates relative to the supply plate 46. Thus, the state in which the through hole 50c of the sliding plate 50 is connected to the through hole 46a of the supply plate 46 is switched. Due to the oscillating rotation of the oscillating gear 5, the high-pressure chamber 66a also deviates slightly in the rotational direction relative to the low-pressure chamber 66b.

[0209] When the state of communication between the through hole 50c of the sliding plate 50 and the through hole 46a of the supply plate 46 is switched, working oil is supplied to the high-pressure chamber 66a again. Then, working oil is discharged from the low-pressure chamber 66b. By repeating this action, the rotating part 3 rotates relative to the swing housing part 2. Output is obtained using this rotation.

[0210] When the through hole 46a comes to the position aligned with the through hole 50c due to the rotation of the sliding plate 50 and the supply plate 46, the working oil is discharged from the low-pressure working chamber 66b to the through hole 50c.

[0211] Furthermore, when the through hole 46a and the through hole 50c are not aligned and connected, the through hole 46a is blocked by the sliding plate 50 to prevent working oil from being discharged from the working chambers 66a and 66b through the through hole 46a.

[0212] The piston 51 at the discharge opening 42a of the discharge path 42 slides relative to the sliding plate 50, which rotates integrally with the first gear carrier 31, while being forced towards the sliding plate 50 by the spring 51s. When the through hole 50c reaches the position aligned with the piston 51 due to the rotation of the sliding plate 50, the working oil discharged from the through hole 46a is discharged into the discharge path 42 via the piston 51 at the discharge opening 42a. Then, the working oil discharged into the discharge path 42 flows back to the tank via the flow paths 112 and 114 of the distribution plate 100 and the oil distribution section 45.

[0213] In other words, such as Figures 5-7 As shown, the working oil discharged to each discharge path 42 flows into the distribution plate 100 from the opening at the first end 35a of the circular plate portion 35. Therefore, the working oil flows into the through flow path 103 through the opening of the end face 102.

[0214] In the through flow path 103, which has an outer peripheral connecting groove flow path 104 formed on the end face 102, the working oil that flows in from the corresponding discharge path 42 flows into the outer peripheral connecting groove flow path 104 of the end face 102 via the through flow path 103 and merges.

[0215] In the distribution plate 100, the working oil that has been drawn together in the flow path 104 of the connecting groove on the outer periphery of the end face 102 flows into the through flow path 103 that communicates with the flow path 112 at the end face 101. In the distribution plate 100 of this embodiment, the working oil flows from the five through flow paths 103 to the through flow path 103 that communicates with the flow path 112 via the flow path 104 of the connecting groove on the outer periphery of the end face 102.

[0216] The working oil flows along the thickness direction of the distribution plate 100 in the through flow path 103, and then is discharged from the through flow path 103 with an opening in the end face 101 to the flow path 112 through the opening in the end face 45a.

[0217] Similarly, in the through flow path 103, which has an outer peripheral connecting groove flow path 104 formed on the end face 101, the working oil flowing in from the corresponding discharge path 42 flows along the thickness direction of the distribution plate 100 in the through flow path 103. The working oil reaching the end face 101 flows from the outer diameter direction groove flow path 106 of the end face 101 to the outer peripheral connecting groove flow path 104 of the end face 101 via the through flow path 103 and merges. In the distribution plate 100 of this embodiment, the working oil merges from the five through flow paths 103 into the through flow path 103 communicating with the flow path 114 via the outer peripheral connecting groove flow path 104 of the end face 101.

[0218] In the distribution plate 100, the working oil that merges with the flow path 104 at the outer periphery of the end face 101 flows into the through flow path 103 that is connected to the flow path 114 at the end face 101.

[0219] The working oil is then discharged from the through flow path 103, which opens at the end face 101, through the opening at the end face 45a to the flow path 114.

[0220] In multiple discharge paths 42 and flow paths 112 and 114, the same pressure P2 is set to discharge the working oil. Furthermore, in Figures 5-7 , Figure 11 In this context, the supplied working oil (fluid) is set to a low-pressure state, denoted by P2.

[0221] Thus, the working oil discharged from the working chamber 66b via each discharge path 42 merges in the distribution plate 100 and is discharged into the flow paths 112 and 114.

[0222] Thus, the hydraulic motor 1 utilizes the inconsistency between the number of supply paths 41 (supply opening 41a and through holes 50c of sliding plate 50 communicating with supply opening 41a) and the number of through holes 46a of supply and discharge plate 46, and the inconsistency between the number of discharge paths 42 (discharge opening 42a and through holes 50c of sliding plate 50 communicating with discharge opening 42a) and the number of through holes 46a of supply and discharge plate 46, thereby sequentially switching the communication state between through holes 50c of sliding plate 50 and through holes 46a of supply and discharge plate 46 in the circumferential direction.

[0223] As a result, working oil is selectively supplied and discharged from each through hole 46a of the supply plate 46 relative to each working chamber 66a, 66b, causing the rotating part 3 to rotate.

[0224] The gear carrier portion 6 constituting the rotating part 3 is divided into a first gear carrier 31 and a second gear carrier 32. The first gear carrier 31 and the second gear carrier 32 are fixed by a fastening bolt 53. Therefore, power transmission between the first gear carrier 31 and the second gear carrier 32 is carried out by means of the fastening bolt 53. The shank portion 53a of the fastening bolt 53 is arranged across the first gear carrier 31 and the second gear carrier 32. Therefore, compared with the case where the external thread portion 53b is across the first gear carrier 31 and the second gear carrier 32, power transmission between the first gear carrier 31 and the second gear carrier 32 is carried out more efficiently.

[0225] Furthermore, the working oil supplied to each chamber 66a, 66b leaks through a small gap between the crankshaft 4 and the oscillating gear 5 into a small gap between each gear carrier 31, 32 and the crankshaft 4. This leaked working oil is discharged through the shaft support recess 44 formed in the first gear carrier 31 into the drain passage (tank path) 43. The working oil discharged into the drain passage (tank path) 43 flows back into a tank (not shown).

[0226] On the first direction side of the oscillating gear 5, the third labyrinth 49 is formed by the first outer peripheral surface 33d of the first gear carrier 31, the second end 33b, and the plate-side labyrinth portion 48 of the feed plate 46. On the second direction side of the oscillating gear 5, the second labyrinth 40 is formed by the second gear carrier-side first labyrinth portion 25 of the second oscillating housing 8 and the second gear carrier-side second labyrinth portion 57 of the second gear carrier 32.

[0227] Therefore, the working oil leaking from the working chambers 66a and 66b through the tiny gap between the crankshaft 4 and the oscillating gear 5 is unlikely to leak out between the first oscillating housing 7 and the first gear carrier 31, and between the second oscillating housing 8 and the second gear carrier 32.

[0228] Furthermore, in the hydraulic motor 1, output can be obtained from the rotating part 3 by fixing the swing housing part 2. In this case, the external device fixed to the outer flange part 39 of the rotating part 3 (first gear carrier 31) becomes the rotated object.

[0229] Furthermore, output can also be obtained from the swing housing 2 by fixing the rotating part 3. In this case, the external device fixed to the outer flange 9 of the swing housing 2 (first swing housing 7) becomes the rotating body.

[0230] The hydraulic motor 1 has an internal gear pin 90 disposed in the first oscillating housing 7. The rotating part 3 includes: a gear carrier part 6; a crankshaft 4 rotatably supported on the gear carrier part 6; and an oscillating gear 5, which is restricted to oscillating rotation by the crankshaft 4 and meshes with the internal gear pin 90. With this configuration, working oil is supplied and discharged to the working chambers 66a and 66b formed between the inner peripheral surface 7c of the first oscillating housing 7 and the outer peripheral surface of the oscillating gear 5, thereby enabling the hydraulic motor 1 to be driven to rotate. With this rotational drive, a higher torque can be obtained. The segmented oscillating housing part 2 can be preferably used in such a hydraulic motor 1.

[0231] The hydraulic motor 1 has a supply and discharge plate 46 for selectively supplying and discharging working oil relative to each working chamber 66a, 66b. The supply and discharge plate 46 is disposed at the first end 10b of the thick-walled portion 10 (the first direction side end of the oscillating gear 5). The supply and discharge plate 46 is fixed to the first oscillating housing 7 by bolts 20. Since the supply and discharge plate 46 is also fixed by bolts 20 used to fix the first oscillating housing 7 and the second oscillating housing 8, the number of components of the hydraulic motor 1 can be reduced.

[0232] In the hydraulic motor 1 of the above embodiment, the working oil supplied from the hydraulic pump to the oil distribution section 45 is distributed to the supply paths 41 in the distribution plate 100 via flow paths 111 and 113 and supplied to the working chambers 66a and 66b. Moreover, the working oil discharged from the working chambers 66a and 66b via the discharge paths 42 merges in the distribution plate 100 and is discharged into flow paths 112 and 114.

[0233] According to the hydraulic motor 1, the distribution plate 100 has: a through flow path 103 that connects end face 101 and end face 102; and connecting groove flow paths 104 to 107, which are formed as grooves on end faces 101 and 102. These third flow paths 103 to 107 are sandwiched in such a way that the end face 45a of the oil distribution section 45, which serves as the first housing, is in close contact with end face 101, and the first end 35a of the circular plate portion 35, which serves as the second housing, is in close contact with end face 102, thereby sealing the grooves. Therefore, the working oil (fluid) can be easily flowed using the distribution plate 100.

[0234] Therefore, the distribution plate 100 connects the first flow paths 111-114 with the second flow paths 41 and 42. The distribution plate 100 can be used to distribute and merge the working oil (fluid) between the first flow paths 111-114 and the second flow paths 41 and 42, which are more numerous than the first flow paths 111-114.

[0235] Therefore, in both the second and first directions, the working oil can be distributed and merged between the first flow paths 111-114 and the second flow paths 41 and 42 using only the thickness of the distribution plate 100. Thus, compared to the prior art described above, the size of the hydraulic motor 1 along the first axis C1 can be reduced.

[0236] Therefore, in a hydraulic motor 1 of the same size, the output torque can be increased. Alternatively, in a hydraulic motor 1 with the same output torque, space can be saved by miniaturizing it in the direction of the first axis C1.

[0237] In the distribution plate 100, connecting groove flow paths 104 to 107 are formed on the end faces 101 and 102 on both sides of its back surface. This allows for the distribution and merging of working oil into up to four independent flow paths. Consequently, it enables one-speed operation (supplying working oil from one flow path 111 to the supply path 41) and two-speed operation (supplying working oil from two flow paths 111 and 113 to the supply path 41).

[0238] In speed 1 operation, working oil is discharged from discharge path 42 into one flow path 111. In speed 2 operation, working oil is discharged from discharge path 42 into two flow paths 113. Therefore, no limitation is imposed on the amount of oil discharged.

[0239] Furthermore, connecting groove flow paths 104 to 107 are formed on the end faces 101 and 102, respectively. A sealed flow path can be formed simply by clamping the connecting groove flow paths 104 to 107. Therefore, compared with the previous technology of forming grooves on the circumferential surface, the sealing performance can be greatly improved.

[0240] In the distribution plate 100, a plurality of through flow paths 103 arranged in the circumferential direction are arranged on the end faces 101, 102 at equal intervals. Thus, as a track motor, the through flow paths 103 can be connected to the supply path 41 and the discharge path 42 arranged alternately in the circumferential direction.

[0241] In the distribution plate 100, multiple through flow paths 103 are connected by an outer peripheral connecting groove flow path 104 and an inner peripheral connecting groove flow path 105. Thus, by simply having the through flow path 103 pass through the flat circular plate and forming the outer peripheral connecting groove flow path 104 and the inner peripheral connecting groove flow path 105 in an annular groove shape on the end face, which is a plane, an independent flow path can be formed by selecting a through flow path 103 at a predetermined position. Therefore, even when the pressures are different, flow splitting and merging can be easily achieved.

[0242] Therefore, when manufacturing the distribution plate 100, the above-described structure can be easily formed by machining a flat circular plate or by casting. In addition, since a high level of sealing can be maintained by clamping the first outer shell and the second outer shell, it is not necessary to have such high machining precision on the end faces 101 and 102.

[0243] In the distribution plate 100, by pre-setting the position of the through flow path 103 forming the outer diameter direction groove flow path 106 and the inner diameter direction groove flow path 107, the through flow path 103 connected to the outer peripheral connecting groove flow path 104 and the inner peripheral connecting groove flow path 105 can be selected. Therefore, the working oil can be distributed and merged as separate independent flow paths.

[0244] In particular, the outer diameter channel flow path 106 and the inner diameter channel flow path 107 are respectively connected to the adjacent through flow paths 103 arranged along the circumferential direction. Therefore, the second housing can be configured to connect the flow paths 111 to 114 to perform flow splitting and merging, corresponding to the supply path 41 and discharge path 42 which are adjacent to each other as different pressures.

[0245] Alternatively, the outer diameter channel flow path 106 and the inner diameter channel flow path 107 can be connected to the through flow paths 103 arranged circumferentially, with each through flow path 103 being adjacent to the other. Therefore, it is possible to configure a structure that connects flow paths 111 and 113 to the high-pressure supply path 41 and discharge path 42, which are supply paths and discharge paths with different pressures, to perform flow splitting and merging. Moreover, it is possible to configure a structure that connects flow paths 112 and 114 to the low-pressure discharge path 42 to perform flow splitting and merging.

[0246] Thus, the formation positions of the outer diameter direction groove flow path 106 and the inner diameter direction groove flow path 107 allow for the flexibility to select flow paths for merging and splitting. In other words, the formation positions of the outer diameter direction groove flow path 106 and the inner diameter direction groove flow path 107 can be used to freely set up four independent flow paths and connect them to the second flow path.

[0247] In this case, the circumferential arrangement of the outer diameter direction groove flow path 106 and the inner diameter direction groove flow path 107 is repeated in groups of four adjacent through flow paths 103 in the circumferential direction, thereby allowing four independent flow paths to be freely set and connected to the second flow path. Furthermore, the circumferential arrangement of the outer diameter direction groove flow path 106 and the inner diameter direction groove flow path 107 is repeated in groups of two adjacent through flow paths 103 in the circumferential direction, thereby allowing two independent flow paths to be freely set and connected to the second flow path on a single side of the end faces 101 and 102 of the distribution plate 100.

[0248] In the above embodiments, the case where bolts 20 are used as fixing parts for securing the first swing housing 7 and the second swing housing 8 has been described. The case where tight-fitting bolts 53 are used as fixing parts for securing the first gear carrier 31 and the second gear carrier 32 has also been described. However, this is not a limitation; any method that can replace bolts 20 and tight-fitting bolts 53 for securing the swing housings 7 and 8 and the gear carriers 31 and 32 is acceptable. For example, rivets or the like can also be used as fixing parts.

[0249] In the above embodiment, the case where the supply plate 46 is fixed to the first swing housing 7 using bolts 20 has been described. However, it is not limited to this; the supply plate 46 may also be fixed to the first swing housing 7 using a different fixing member than bolts 20. In addition, the supply plate 46 may not be fastened together with the first swing housing 7 and the second swing housing 8.

[0250] In this case, an outer flange for fixing the swing housing can be provided on the outer peripheral surface of each swing housing 7, 8, and the outer flange can be fixed with bolts, thereby making each swing housing 7, 8 an integral unit.

[0251] In the above embodiment, the following situation was described: the rotating part 3 has three crankshafts 4, which are used to restrict the oscillating gear 5 to oscillating rotation. However, it is not limited to this; the rotating part 3 may have at least one crankshaft 4.

[0252] In this case, crankshaft 4 becomes a so-called central crankshaft, whose second axis C2 coincides with the first axis C1 of rotating part 3. The rotation of oscillating gear 5 is limited by this central crankshaft.

[0253] In the above embodiment, the pressure state of the working oil is described as a higher pressure P1 and a lower pressure P2, but the pressure states in the first flow paths 111 to 114 can also be set to different values.

[0254] For example, such as Figure 12As shown, the pressure states in flow paths 111-114 are set as pressure P1, pressure P2, pressure P3, and pressure P4, which can be distributed to the four through flow paths 103 arranged circumferentially on the distribution plate 100. In this case, pressure P1, pressure P2, pressure P3, and pressure P4 can be set to all different values, or two of pressure P1, pressure P2, pressure P3, and pressure P4 can be set to the same value, and the remaining two can be set to different values, thus setting three values. Moreover, three of pressure P1, pressure P2, pressure P3, and pressure P4 can be set to the same value, thus setting two values.

[0255] In the embodiments disclosed in this specification, a component composed of multiple objects can be made into one integrated object; conversely, a component composed of a single object can be divided into multiple objects. Regardless of whether it is integrated or not, it can be constructed in a manner that achieves the purpose of the invention.

Claims

1. A fluid device, wherein, This fluid device has the following features: A first outer casing having a first flow path; A second housing having a greater number of second flow paths than the number of first flow paths; and A distribution board having a third flow path that connects the predetermined first flow path to the second flow path. The distribution plate is sandwiched between the first and second outer shells in the thickness direction, with its end faces in contact with the first and second outer shells respectively. The third flow path has: Multiple through flow paths are arranged circumferentially to extend through the thickness direction of the distribution plate and open at the end face. as well as A connecting channel flow path, formed circumferentially, connects multiple through flow paths in the distribution plate. The distribution plate is clamped between the first and second housings in a manner that does not rotate relative to the second housing. The openings of the plurality of through flow paths are respectively connected to the corresponding second flow path.

2. The fluid device according to claim 1, wherein, The connecting groove flow path is formed on the end face of the distribution plate.

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

4. The fluid device according to claim 1 or 2, wherein, The connecting groove flow path has: An outer peripheral connecting groove flow path, positioned radially outward from the plurality of through flow paths, connects the plurality of through flow paths; and An inner circumferential connecting groove flow path is positioned radially inward than the plurality of through flow paths, connecting the plurality of through flow paths.

5. The fluid device according to claim 4, wherein, The third flow path also has: An outer diameter-oriented groove flow path, formed radially on the end face, radially connecting the through flow path and the outer peripheral connecting groove flow path; and An inner diameter directional groove flow path, formed radially on the end face, connects the through flow path and the inner circumferential connecting groove flow path radially. The outer diameter channel flow path and the inner diameter channel flow path are respectively connected to the through flow paths that are adjacent to each other in the circumferential direction, or respectively connected to the through flow paths that are adjacent to each other in the circumferential direction with one through flow path in between.

6. The fluid device according to claim 5, wherein, The outer diameter direction groove flow path and the inner diameter direction groove flow path are configured to repeat in groups of two or four adjacent through flow paths in the circumferential direction.

7. The fluid device according to claim 4, wherein, The inner circumferential connecting groove flow path, the plurality of through flow paths, and the outer circumferential connecting groove flow path are respectively arranged on concentric circles on the end face.

8. The fluid device according to claim 4, wherein, The second outer casing includes: The swing housing portion has an axis; Internal teeth are provided on the inner circumferential surface of the swing housing portion; The gear carrier is supported on the swing housing by means of two bearings that are arranged separately from each other along the axis of the swing housing in a manner that allows it to rotate freely about the axis; A crankshaft, which is rotatably supported on the gear carrier about another axis parallel to the said axis; The oscillating gear, whose rotational motion is restricted to oscillating rotation by the crankshaft, meshes with the internal gear; as well as The fluid supply and discharge plate has multiple supply and discharge channels for supplying working fluid between the inner peripheral surface of the swing housing and the swing gear, and for discharging working fluid from the inner peripheral surface of the swing housing and the swing gear. The supply and discharge plate is disposed on the first housing side of the oscillating gear along the axis, and the plurality of supply and discharge flow paths are respectively connected to the second flow path.

9. The fluid device according to claim 8, wherein, The inner circumferential connecting groove flow path and the outer circumferential connecting groove flow path supply and discharge working fluids at different pressures, or supply and discharge working fluids at the same pressure.

10. A fluid device, wherein, This fluid device has the following features: A first outer casing having a first flow path; A second housing having a greater number of second flow paths than the number of first flow paths; and A distribution board having a third flow path that connects the predetermined first flow path to the second flow path. The distribution plate is sandwiched between the first and second outer shells in the thickness direction, with its end faces in contact with the first and second outer shells respectively. The second outer casing includes: The swing housing portion has an axis; Internal teeth are provided on the inner circumferential surface of the swing housing portion; The gear carrier is supported on the swing housing by means of two bearings that are arranged separately from each other along the axis of the swing housing in a manner that allows it to rotate freely about the axis; A crankshaft, which is rotatably supported on the gear carrier about another axis parallel to the said axis; The oscillating gear, whose rotational motion is restricted to oscillating rotation by the crankshaft, meshes with the internal gear; as well as The fluid supply and discharge plate has multiple supply and discharge channels for supplying working fluid between the inner peripheral surface of the swing housing and the swing gear, and for discharging working fluid from the inner peripheral surface of the swing housing and the swing gear. The supply and discharge plate is disposed on the first housing side of the oscillating gear along the axis, and the plurality of supply and discharge flow paths are connected to the second flow path. The third flow path has: Multiple through-flow paths are arranged circumferentially and open at the end face; The outer peripheral connecting groove flow path, which serves as a connecting groove flow path connecting multiple through flow paths, is formed circumferentially on the end face and connects multiple through flow paths at a position radially outward compared to the multiple through flow paths. An inner circumferential connecting groove flow path, which serves as the connecting groove flow path, is formed circumferentially on the end face, and connects the plurality of through flow paths at a position radially inward compared to the plurality of through flow paths. An outer diameter direction groove flow path is formed on the end face in a radial manner, connecting the through flow path and the outer peripheral connecting groove flow path in a radial direction; as well as An inner diameter directional groove flow path, formed radially on the end face, connects the through flow path and the inner circumferential connecting groove flow path radially. The outer diameter direction groove flow path and the inner diameter direction groove flow path are respectively connected to the through flow paths that are adjacent to each other in the circumferential direction, or the outer diameter direction groove flow path and the inner diameter direction groove flow path are respectively connected to the through flow paths that are adjacent to each other in the circumferential direction with one through flow path in between. The configuration of the outer diameter direction groove flow path and the inner diameter direction groove flow path is repeated in groups of four through flow paths that are adjacent to each other in the circumferential direction.

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