Rotating machinery

Abstract

To has a compact and certain brake function.SOLUTION: Rotary equipment 1 is equipped with a housing portion 2 that has an axis line C1, internal teeth 90 provided on an inner peripheral surface of the housing portion, a carrier portion 6 supported by the housing portion so as to rotate around the axis line, a crank shaft 4 supported by the carrier portion so as to rotate around the other axis line C2 in parallel with the axis line, a rocking gear 5 regulated by the crank shaft so as to rock and rotate and engaged with the internal teeth, a plurality of supply / discharge channels 41 and 42 supplying working fluid into between an inner peripheral surface of the housing portion and the rocking gear and discharging the working fluid from a space between the inner peripheral surface of the housing portion and the rocking gear, a stopper 102 moving so as to contact with and separate from either one of the rocking gear and the crank shaft, and a stopper moving portion pressing the stopper against the rocking gear or releasing the pressing so that the stopper moves so as to contact with or separate from the rocking gear or the crank shaft.SELECTED DRAWING: Figure 1

Description

Technical Field

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[0001] The present invention relates to a rotating device.

Background Art

[0002] As hydraulic pumps and motors, those described in Patent Documents 1 and 2 are known. Here, it is a parking brake that stops the operation by restricting the swing of the swing member. As a parking brake, for example, Patent Document 1 describes a configuration in which a brake pin 60 that becomes a lock position for suppressing the swing of a star gear 30 is moved to a non-lock position by a brake rod 72 to release the lock.

[0003] Although the technique of inserting a regulating shaft into the central hole of a swing gear has existed for a long time, improvements have been made regarding the method of moving the regulating shaft and the oil passage.

Prior Art Documents

Patent Documents

[0004]

Patent Document 1

Patent Document 2

Summary of the Invention

[0007] A rotating device according to one aspect of the present invention is A housing section having an axis, The internal teeth provided on the inner circumferential surface of the housing portion, A carrier portion is supported in the housing portion so as to be rotatable around the axis, A crankshaft is supported in the carrier portion so as to be rotatable around another axis parallel to the aforementioned axis, A rocking gear whose rotation is restricted by the crankshaft and which meshes with the internal teeth, Multiple supply and discharge channels are provided to supply working fluid between the inner circumferential surface of the housing and the oscillating gear and to discharge working fluid from between the inner circumferential surface of the housing and the oscillating gear. A stopper that can move so as to be able to contact and separate from either the oscillating gear or the crankshaft, The stopper moving part presses or releases the stopper toward the oscillating gear so that the stopper can move toward and away from the oscillating gear or the crankshaft, The above problem was solved by incorporating the following features.

[0008] With this configuration, the rotation of the rotating equipment can be stopped by using the stopper to stop the rotation of either the oscillating gear or the crankshaft. In this way, by driving the stopper with a stopper movement part, the stopper can be used as a brake for the rotating equipment. Therefore, it is possible to provide rotating equipment with a simple structure and a compact braking mechanism.

[0009] In the above configuration, the stopper holds down the oscillating gear and stops its oscillating rotation. It is possible.

[0010] In the above configuration, the stopper moving part moves the stopper along the rotation axis direction of the oscillating gear. It is possible.

[0011] In the above configuration, the crankshafts are arranged in the circumferential direction around the axis, The stopper is located near the center of the oscillating gear. It is possible.

[0012] In the above configuration, the stopper is supported by the carrier portion. It is possible.

[0013] In the above configuration, an eccentric stopper engagement portion is formed on the oscillating gear, and the stopper moving portion inserts the stopper into the stopper engagement portion to stop the oscillating rotation. It is possible.

[0014] In the above configuration, the stopper moving part is A pressing portion that presses against the stopper and inserts into the stopper engagement portion to stop the oscillating rotation of the oscillating gear, A release unit that releases the pressing state of the pressing portion against the stopper using a working fluid and removes the stopper from the stopper engagement portion, Equipped with, It is possible.

[0015] In the above configuration, two bearings are provided spaced apart from each other along the axis of the housing portion to support the carrier portion relative to the housing portion, A supply and discharge plate is positioned adjacent to the oscillating gear along the axial direction, having a plurality of supply and discharge channels for supplying working fluid to an operating chamber formed between the inner circumferential surface of the housing and the oscillating gear, and for discharging working fluid from the operating chamber formed between the inner circumferential surface of the housing and the oscillating gear, The carrier portion is formed and each of the multiple supply and discharge passages leads to the outside, and the branch passage is branched from the fluid supply passage to the working chamber and leads to the release section. comprises, The pressing force of the pressing portion against the stopper is released by the working fluid supplied to the pressing release portion through the branch flow path. It can be done.

[0016] According to the rotating device according to another aspect of the present invention, a housing portion having an axis, internal teeth provided on the inner peripheral surface of the housing portion, a carrier portion rotatably supported around the axis of the housing portion via two bearings provided apart from each other along the axis of the housing portion, a crankshaft rotatably supported around another axis parallel to the axis on the carrier portion and arranged in the circumferential direction around the axis, a swing gear that is regulated by the crankshaft to swing and rotate and meshes with the internal teeth, a supply / discharge plate having a plurality of supply / discharge flow paths for supplying the working fluid to the working chamber formed between the inner peripheral surface of the housing portion and the swing gear and discharging the working fluid from the working chamber formed between the inner peripheral surface of the housing portion and the swing gear, and arranged adjacent to the swing gear along the axial direction, a stopper supported by the carrier portion, located near the center of the swing gear, and movable into contact with and away from the swing gear, a stopper engaging portion formed eccentrically on the swing gear, a stopper moving portion that presses or releases the pressing of the stopper toward the stopper engaging portion so that the stopper can move into contact with and away from the stopper engaging portion of the swing gear, flow paths formed in the carrier portion and each leading to the outside of the plurality of supply / discharge flow paths, a branch flow path branched from the supply path of the working fluid to the working chamber among the flow paths and leading to the stopper moving portion, comprises, The stopper moving hand portion is A pressing portion that presses against the stopper and inserts into the stopper engagement portion to stop the oscillating rotation of the oscillating gear, A release unit that releases the pressing state of the pressing portion against the stopper by using the working fluid supplied through the branched passage to remove the stopper from the stopper engagement portion, Having, It is possible.

[0017] With this configuration, the drive of the rotating equipment can be stopped by inserting the stopper into the stopper engagement portion of the oscillating gear and stopping the oscillating rotation of the oscillating gear. At this time, when supplying working fluid to the working chamber to drive the rotating equipment, the fluid is supplied to the release portion of the stopper movement portion via a branched flow path that branches off from the supply path, thereby releasing the restriction on the oscillating gear by the stopper inserted into the stopper engagement portion by the pressing portion, and releasing the restriction on the position of the oscillating gear. In this way, by driving the stopper with the stopper movement portion, the stopper can be used as a parking brake that is released when the rotating equipment is driven and brakes when it is not driven. Therefore, it is possible to provide rotating equipment with a simple structure and a compact parking brake mechanism. [Effects of the Invention]

[0018] According to the present invention, it is possible to provide a rotating device with a parking brake function that has a simple structure, high durability, and can be miniaturized. [Brief explanation of the drawing]

[0019] [Figure 1] This is a partially cross-sectional side view showing a first embodiment of a hydraulic motor according to the present invention. [Figure 2] This is a cross-sectional view along the line II-II in Figure 1. [Figure 3] This is an enlarged view of part III of Figure 1. [Figure 4] This is an enlarged view of section VI in Figure 1. [Figure 5] This is an enlarged view of section V showing the release state in Figure 1. [Figure 6] This is an enlarged view showing the engagement state in Figure 5. [Figure 7] This is an enlarged view showing the release state corresponding to section V in Figure 1 in a second embodiment of the hydraulic motor according to the present invention. [Figure 8] This is an enlarged view showing the engagement state in Figure 7. [Modes for carrying out the invention]

[0020] Hereinafter, a first embodiment of the rotating device according to the present invention will be described with reference to the drawings. Figure 1 is a partially cross-sectional side view showing a hydraulic motor as an example of a rotating device in this embodiment. Figure 2 is a cross-sectional view along the line II-II in Figure 1. Figure 3 is an enlarged view of part III in Figure 1. Figure 4 is an enlarged view of part IV in Figure 1. In the figures, reference numeral 1 denotes a hydraulic motor.

[0021] In this embodiment, the rotating device will first be described as a hydraulic motor.

[0022] <Hydraulic motor> As shown in Figures 1 to 4, the hydraulic motor 1 mainly consists of a cylindrical housing portion 2, a rotating portion 3 rotatably supported on the inner circumferential surface of the housing portion 2 via two bearings 12 and 13 (first bearing 12, second bearing 13), and a brake mechanism 100. Angular contact ball bearings are used as bearings 12 and 13. However, they are not the only type of bearing that can be used; various other types of ball bearings, such as deep groove ball bearings or sliding bearings, can also be used.

[0023] The central axis of the housing 2 and the rotation axis of the rotating part 3 coincide. In the following description, these central axis and rotation axis will be collectively referred to as the first axis (an example of an axis in the claims) C1. In addition, the direction parallel to the first axis C1 may be simply referred to as the axial direction, the rotation direction of the rotating part 3 as the circumferential direction, and the radial direction of the rotating part 3 as the radial direction.

[0024] <Housing Department> The housing section 2 is divided axially and consists of a first housing 7 located on the first axial direction side (left side in Figure 1) and a second housing 8 located on the second axial direction side (right side in Figure 1) opposite to the first axial direction. Note that the housing section 2 can also be configured without being divided axially. The first housing 7 is formed in a cylindrical shape. An outer flange portion 9 is formed on the outer circumferential surface 7a of the first housing 7, near the first end 7b on the first direction side, and protrudes radially outward. The outer flange portion 9 is for attaching the hydraulic motor 1 to external equipment (not shown). A through hole 9a for passing a bolt (not shown) is formed through the outer flange portion 9 in the thickness direction (axial direction) of the outer flange portion 9.

[0025] Of the peripheral wall 7e of the first housing 7, the section from the second end 7d on the second direction side to the axial center is a thicker section 10 than other parts. The second end 10c on the second direction side of the thicker section 10 is located on the same plane as the second end 7d of the first housing 7. In other words, the second end 10c of the thicker section 10 constitutes a part of the second end 7d of the first housing 7.

[0026] Multiple 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 and extends across the entire thickness of the thick-walled portion 10, and is arranged at equal intervals in the circumferential direction. The pin grooves 10a are formed in a semicircular shape when viewed from the axial direction. A cylindrical internal tooth pin (an example of an internal tooth according to the claim) 90 is rotatably housed in each pin groove 10a. Because the pin grooves 10a are formed in a semicircular shape when viewed from the axial direction, the internal tooth pin 90 protrudes radially inward by a semicircular distance from the inner circumferential surface 10d of the thick-walled portion 10. The internal tooth pin 90 functions as an internal tooth that meshes with the oscillating gear 5, which will be described later.

[0027] On the outer circumference of the thickened portion 10, first through holes 19 are formed between each pin groove 10a, penetrating in the axial direction. The first through holes 19 are arranged at equal intervals in the circumferential direction. For example, there are eight first through holes 19. The shaft portion 20a of a bolt (an example of a fixing portion and screw) 20 is inserted into these first through holes 19. The first housing 7, the second housing 8, and the supply / discharge plate 46, described later, are fastened together by each bolt 20 and integrated into one unit.

[0028] Furthermore, a first bearing housing 11 is formed on the inner circumferential surface 7c of the first housing 7, with a larger inner diameter via a stepped portion 11a, closer to the first direction than the thickened portion 10. The outer race 12a of the first bearing 12 is fitted into this first bearing housing 11. Positioning of the first bearing 12 and the first housing 7 is achieved by the outer race 12a abutting against the stepped portion 11a.

[0029] On the inner circumferential surface 7c of the first housing 7, a seal housing portion 14 is formed with a larger inner diameter via a stepped portion 14a, closer to the first direction than the first bearing housing portion 11. A part of the seal portion 15 is fitted into this seal housing portion 14. The seal portion 15 seals the space between the first housing 7 and the rotating portion 3. For example, a floating seal can be used as the seal portion 15. However, it is not limited to this, and various seals such as packings and mechanical seals can be used.

[0030] The first end 7b of the first housing 7 has a first carrier-side first labyrinth section 16 formed therein, which has a larger inner diameter than the seal storage section 14. The first carrier-side first labyrinth section 16 works in cooperation with the rotating section 3 to form a first labyrinth 38. The first labyrinth 38 makes it difficult for dust and other debris to enter the space between the first housing 7 and the rotating section 3 from the outside.

[0031] The second end 7d of the first housing 7 corresponds to the dividing surface between the first housing 7 and the second housing 8 of the housing portion 2. The entire outer circumference of the second end 7d of the first housing 7 is formed flat. Closer to the outer circumference of the second end 7d than the first through hole 19, an annular O-ring groove 17 is formed when viewed from the axial direction. An O-ring 18 is fitted into the O-ring groove 17. The O-ring 18 ensures a seal between the first housing 7 and the second housing 8.

[0032] The second housing 8 is formed in an annular shape. A second through-hole 22 is formed in the peripheral wall 8a of the second housing 8 at a position corresponding to the first through-hole 19 of the first housing 7, and is connected to the first through-hole 19. The second through-hole 22 is formed with the same diameter as the first through-hole 19 and is located coaxially with the first through-hole 19. A counterbore 23 is formed in most of the second direction side of the second through-hole 22. The head 20b of the bolt 20 is inserted into the counterbore 23.

[0033] The first end portion 8b of the second housing 8 on the first direction side corresponds to the dividing surface between the housing portion 2 and the first housing 7. A retaining plate 21 is integrally molded to the first end portion 8b of the second housing 8, protruding radially inward from the inner circumferential surface 8c of the second housing 8. The retaining plate 21 is formed in an annular shape when viewed from the axial direction. The retaining plate 21 closes the working chambers 66a and 66b formed between the inner circumferential surface 7c of the first housing 7 and the outer circumferential surface of the oscillating gear 5, which will be described later, from the second direction side. Furthermore, the retaining plate 21 can be formed separately from the housing portion 2 when the first housing 7 and the second housing 8 are integrated.

[0034] The inner circumferential surface 21a of the retaining plate 21 has a second carrier-side first labyrinth portion 25 formed on most of it, excluding the end on the first direction side. The second carrier-side first labyrinth portion 25 is formed by making the inner diameter larger than the inner diameter of the inner circumferential surface 21a of the retaining plate 21 via a stepped portion 25a. The second carrier-side first labyrinth portion 25 works in cooperation with the rotating portion 3 to form a second labyrinth 40. The second labyrinth 40 makes it difficult for hydraulic fluid to leak from between the second housing 8 and the rotating portion 3 (details will be described later).

[0035] On the inner circumferential surface 8c of the second housing 8, a second bearing housing portion 24 is formed, with a larger inner diameter via a stepped portion 24a, closer to the second direction than the retaining plate 21. The outer race 13a of the second bearing 13 is fitted into this second bearing housing portion 24. Positioning of the second bearing 13 and the second housing 8 is achieved by the outer race 13a abutting against the stepped portion 24a.

[0036] An annular O-ring groove 26 is formed on the outer circumference of the second end 8d on the second direction side of the second housing 8 when viewed from the axial direction. An O-ring 27 is fitted into the O-ring groove 26. The O-ring 27 ensures a seal between the second housing 8 and the cover 29, which will be described later. At the second end 8d of the second housing 8, multiple female threaded portions 28 are formed radially inward from the O-ring groove 26 and are spaced equally in the circumferential direction. These female threaded portions 28 are for fixing the cover 29 to the second housing 8.

[0037] <Cover> The cover 29 closes the opening 8e of the second housing 8 from the second direction side. The cover 29 is formed, for example, by press-forming a metal plate so that the majority of the center bulges out toward the second direction side. The outer periphery of the cover 29 has an outer flange portion 29a formed thereon. This outer flange portion 29a overlaps the second end portion 8d of the second housing 8.

[0038] The outer flange portion 29a has a through hole 29b that penetrates in the thickness direction at a position corresponding to the female thread portion 28 of the second housing 8. The cover 29 is fixed to the second housing 8 by inserting a bolt 30 from the second direction side into this through hole 29b and tightening the bolt 30 into the female thread portion 28 of the second housing 8.

[0039] <Intake and Exhaust Plate> The supply and discharge plate (port plate) 46, which is fixed by bolts 20 inserted into the second through hole 22 of the second housing 8 and the first through hole 19 of the first housing 7, is located at the first end 10b on one side of the thickened portion 10. The supply and discharge plate 46 is a plate for supplying hydraulic fluid to the working chambers 66a and 66b, which will be described later, and for discharging hydraulic fluid from the working chambers 66a and 66b.

[0040] The supply and discharge plate 46 is formed in an annular shape when viewed from the axial direction. The outer diameter of the supply and discharge plate 46 is approximately the same as or slightly smaller than the diameter of the inner circumferential surface 7c of the first housing 7. For this reason, the supply and discharge plate 46 is positioned at the first end 10b of the thickened portion 10 so as to fit into the inner circumferential surface 7c of the first housing 7.

[0041] A female threaded portion 47 is formed on the outer circumference of the supply and discharge plate 46 at a position corresponding to the first through hole 19 of the first housing 7. A bolt 20 is inserted from the second housing 8 side in the order of the second through hole 22 and the first through hole 19 of the first housing 7, and the bolt 20 is tightened into the female threaded portion 47 of the supply and discharge plate 46. In this way, the first housing 7, the second housing 8 and the supply and discharge plate 46 are fastened together by each bolt 20 and integrated into one unit.

[0042] The supply and discharge plate 46 has multiple through holes (supply and discharge ports) 46a that penetrate in the thickness direction, radially inward from the female thread portion 47. Hydraulic fluid is supplied to the working chambers 66a and 66b, and hydraulic fluid is discharged from the working chambers 66a and 66b through these through holes 46a (details will be described later). The number of through holes (supply and discharge ports) 46a corresponds to the number of pin grooves 10a formed in the first housing 7. For example, in this embodiment, there are 13 through holes 46a. Each through hole (supply and discharge port) 46a is formed such that the opening on the thickened portion 10 side is in the center between adjacent pin grooves 10a in the circumferential direction, and is located radially inward from the inner circumferential surface 10d of the thickened portion 10.

[0043] A plate-side labyrinth section 48 is formed on the inner circumferential surface 46b of the supply and discharge plate 46, excluding the end in the second direction. The plate-side labyrinth section 48 is formed by making the inner diameter larger than the inner diameter of the inner circumferential surface 46b of the supply and discharge plate 46 via a stepped section 48a. The plate-side labyrinth section 48 works in cooperation with the rotating section 3 to form a third labyrinth 49. The third labyrinth 49 makes it difficult for hydraulic fluid to leak from between the supply and discharge plate 46 and the rotating section 3 (details will be described later).

[0044] <Rotating part> The rotating part 3, which is rotatably held in the housing part 2, mainly consists of a carrier part (rotating member) 6 whose axial sides are rotatably supported via bearings 12 and 13, a plurality of crankshafts 4 (for example, three in this embodiment) rotatably supported by the carrier part 6, and an oscillating gear 5 rotatably supported by the crankshafts 4. The carrier section 6 is divided in the axial direction and consists of a first carrier 31 arranged on the first direction side and a second carrier 32 arranged on the second direction side.

[0045] The first carrier 31 is integrally molded with a disc-shaped substrate portion 33 and a plurality of support columns 34 (for example, three in this embodiment) that protrude in the second direction from the second end portion 33b on the second direction side of the substrate portion 33. The outer circumferential surface 33c of the substrate portion 33 is formed so that its outer diameter gradually increases via a stepped portion from the second end portion 33b toward the first end portion 33a on the first direction side.

[0046] In other words, the outer peripheral surface 33c of the substrate portion 33 has, in order from the second end portion 33b side, a first outer peripheral surface 33d, a second outer peripheral surface 33e with a larger outer diameter formed at the first direction side end of the first outer peripheral surface 33d via a large stepped portion 33h, a third outer peripheral surface 33f with a larger outer diameter formed at the first direction side end of the second outer peripheral surface 33e via a small stepped portion 33i, and a fourth outer peripheral surface 33g with a larger outer diameter formed at the first direction side end of the third outer peripheral surface 33f via a medium stepped portion 33j.

[0047] The portion of the first carrier 31 corresponding to the first outer peripheral surface 33d is inserted into the plate-side labyrinth portion 48 of the supply and discharge plate 46. The outer diameter of the first outer peripheral surface 33d is slightly smaller than the inner diameter of the plate-side labyrinth portion 48. The second end portion 33b of the first carrier 31 is located slightly in front of the stepped portion 48a of the supply and discharge plate 46. In this way, the first outer peripheral surface 33d of the first carrier 31, the second end portion 33b, and the plate-side labyrinth portion 48 of the supply and discharge plate 46 constitute the third labyrinth 49.

[0048] The inner race 12b of the first bearing 12 is fitted onto the third outer surface 33f. Positioning of the first bearing 12 and the first carrier 31 is achieved by the inner race 12b abutting against the intermediate stepped portion 33j. This positions the first carrier 31 relative to the first housing 7. Furthermore, the first carrier 31 is rotatably supported relative to the first housing 7 via the first bearing 12.

[0049] The fourth outer surface 33g of the first carrier 31 faces the seal storage portion 14 of the first housing 7 in the radial direction. In other words, the seal portion 15 is positioned between the fourth outer surface 33g of the first carrier 31 and the seal storage portion 14 of the first housing 7.

[0050] A circular disc portion 35 is integrally molded at the first-direction end of the fourth outer peripheral surface 33g when viewed from the axial direction. The second end portion 35b of the disc portion 35 on the second-direction side faces the first end portion 7b of the first housing 7 in the axial direction. The outer diameter of the disc portion 35 is equal to the diameter of the outer peripheral surface 7a of the first housing 7. An annular seal housing recess 36 is formed on the outer circumference of the second end portion 35b of the disc portion 35 when viewed from the axial direction. The seal housing recess 36 is smoothly connected to the fourth outer peripheral surface 33g. A part of the seal portion 15 is also housed in the seal housing recess 36. This seals the space between the first housing 7 and the first carrier 31 (rotating portion 3).

[0051] At the second end 35b of the disc portion 35, a first carrier-side second labyrinth portion 37 is formed on the outer circumference, with a step separating it from the outer diameter. This first carrier-side second labyrinth portion 37 and the first carrier-side first labyrinth portion 16 formed on the first housing 7 constitute the first labyrinth 38. Since the first labyrinth 38 is positioned radially outward of the seal portion 15, the intrusion of dust and other debris from the outside through the gap between the first housing 7 and the first carrier 31 (rotating portion 3) can be reliably suppressed.

[0052] An outer flange portion 39 is formed on the outer circumferential surface 35c of the disc portion 35, extending radially outward. The outer flange portion 39 is for attaching the hydraulic motor 1 to external equipment (not shown). A through hole 39a for passing a bolt (not shown) is formed through the outer flange portion 39 in the thickness direction (axial direction).

[0053] At the second end 33b of the substrate portion 33, a plurality of shaft support recesses 44 (for example, three in this embodiment) are formed at equal intervals in the circumferential direction, closer to the outer periphery (slightly radially inward from the first outer circumferential surface 33d). The shaft support recesses 44 rotatably support the crankshaft 4. A first bearing 59a for rotatably supporting the crankshaft 4 is fitted into the shaft support recesses 44. The first bearing 59a is, for example, a sliding bearing. However, it is not limited to this, and various bearings such as ball bearings can be used.

[0054] Furthermore, the substrate portion 33 has multiple supply passages 41, multiple discharge passages 42, and a drain passage (tank passage) 43 formed radially inward from the second outer peripheral surface 33e, extending along the entire axial direction of the substrate portion 33. The supply passage 41 is an oil passage through which hydraulic fluid is supplied from a hydraulic pump (not shown). The second direction side end of the supply passage 41 is open via a large stepped section 33h. That is, each supply passage 41 has a supply opening 41a in the large stepped section 33h. The discharge passage 42 is an oil passage through which the hydraulic fluid in the hydraulic motor 1 is discharged. The second direction side end of the discharge passage 42 is also open via a large stepped section 33h. That is, each discharge passage 42 has a discharge opening 42a in the large stepped section 33h.

[0055] The number of supply passages 41 and the number of discharge passages 42 are different from the number of through holes 46a in the supply / discharge plate 46 fixed to the first housing 7. For example, in this embodiment, the number of supply passages 41 and the number of discharge passages 42 are 12 each, which is one less than the number of through holes (supply / discharge ports) 46a in the supply / discharge plate 46. The supply openings 41a of the supply passage 41 and the discharge openings 42a of the discharge passage 42 are arranged alternately in the circumferential direction on the same pitch circle. Each supply opening 41a and each discharge opening 42a are paired and arranged at equal intervals in the circumferential direction.

[0056] The drain passage (tank passage) 43 is a flow path for returning the hydraulic fluid leaked from the hydraulic motor 1 to a tank (not shown). The first-direction ends of the supply passage 41, discharge passage 42, and drain passage 43 are connected to an oil distribution section 45 provided at the first end 33a on the first-direction side of the base portion 33. The oil distribution section 45 has a plurality of distribution channels (not shown). Through these distribution channels, hydraulic fluid from the hydraulic pump is supplied to the supply passage 41. In addition, hydraulic fluid discharged to the discharge passage 42 is returned to the tank via the distribution channels or returned to the supply passage 41 again. Hydraulic fluid discharged to the drain passage 43 is also returned to the tank via the distribution channels. Further details regarding the operation of the hydraulic fluid will be described later.

[0057] A gap is formed between the large stepped portion 33h of the first carrier 31 and the supply / discharge plate (port plate) 46. A sliding plate (piston plate) 50 is positioned in this gap. The sliding plate 50 is formed in an annular shape when viewed from the axial direction. The inner surface of the sliding plate 50 is fitted onto the first outer surface 33d of the first carrier 31, and it is provided so as to be non-rotatable relative to the first carrier 31 and slidable in the axial direction. The thickness of the sliding plate 50 is smaller than the gap between the large stepped portion 33h and the supply / discharge plate 46.

[0058] The sliding plate (piston plate) 50 has multiple through holes (through ports) 50c formed therein, corresponding to the supply opening 41a of the supply passage 41 and the discharge opening 42a of the discharge passage 42. The through holes 50c corresponding to the supply opening 41a are arranged coaxially with the supply opening 41a. The through holes 50c corresponding to the discharge opening 42a are arranged coaxially with the discharge opening 42a.

[0059] A cylindrical piston 51 is provided at each supply opening 41a and each discharge opening 42a. The piston 51 is slidably mounted in the supply passage 41 and the discharge passage 42. The piston 51 is pressed toward the sliding plate 50 by springs (not shown) provided in the supply passage 41 and the discharge passage 42. Therefore, the piston 51 is pressed against the sliding plate (piston plate) 50.

[0060] The thickness of the sliding plate 50 is smaller than the gap between the large stepped portion 33h and the supply / discharge plate 46. Therefore, the piston 51 protrudes from the large stepped portion 33h by the spring and abuts against the sliding plate 50. As a result, the sliding plate 50 is pressed against the supply / discharge plate 46. This allows each supply passage 41 to connect with the through-hole 50c of the sliding plate 50 via the piston 51. Also, each discharge passage 42 to connect with the through-hole 50c of the sliding plate 50 via the piston 51. Furthermore, each through-hole 50c of the sliding plate 50 connects with the through-hole 46a of the supply / discharge plate 46.

[0061] The support columns 34 of the first carrier 31 are columnar in shape, forming a triangular shape when viewed from the axial direction. Each support column 34 is positioned between the axial support recesses 44 of the base plate 33 in the circumferential direction. In other words, each support column 34 is positioned at equal intervals in the circumferential direction on the second end portion 33b of the base plate 33. The pitch circle diameter of each support column 34 and the pitch circle diameter of the axial support recesses 44 are approximately the same.

[0062] The tip 34a of the support column 34 is formed flat. The tip 34a of the support column 34 is located on the same plane as the second end 7d of the first housing 7. A female thread portion 52 for a reamer bolt is formed on the tip 34a of the support column 34.

[0063] The female thread portion 52 for the reamer bolt consists of a fitting recess 52a formed along the axial direction from the tip 34a of the support portion 34 to the axial center of the support portion 34, and a female thread portion body 52b extending in a first direction from the bottom of the fitting recess 52a. By tightening a reamer bolt (an example of another fixing part) 53 into the female thread portion 52 for the reamer bolt, the first carrier 31 and the second carrier 32 are integrated.

[0064] The second carrier 32 is formed in a disc shape. The second carrier 32 is positioned such that its first end portion 32a on the first direction side abuts against the tip portion 34a of the support portion 34 that constitutes the first carrier 31. As a result, a gap equal to the height of the support portion 34 is formed between the base portion 33 of the first carrier 31 and the second carrier 32. The thickened portion 10 of the first housing 7 surrounds this gap, forming a oscillating gear housing portion 60 for housing the oscillating gear 5.

[0065] The first end portion 32a of the second carrier 32 is formed to be flat throughout. The second carrier 32 has a fitting hole 54 that penetrates in the thickness direction at a position corresponding to the female thread portion 52 for the reamer bolt. The first carrier 31 and the second carrier 32 are integrated by inserting the reamer bolt 53 into the fitting hole 54 from the second direction side of the second carrier 32 and tightening this reamer bolt 53 to the female thread portion body 52b via the fitting recess 52a of the support portion 34.

[0066] The reamer bolt 53 consists of a shaft portion 53a, a male threaded portion 53b that protrudes from the first direction side end of the shaft portion 53a and is formed coaxially with the shaft portion 53a, and a head portion 53c that is formed coaxially with the shaft portion 53a at the second direction side end of the shaft portion 53a. When the reamer bolt 53 is tightened into the female threaded portion 52 for the reamer bolt, the shaft portion 53a of the reamer bolt 53 is fitted into the fitting recess 52a of the support portion 34 and the fitting hole 54 of the second carrier 32. That is, the shaft portion 53a of the reamer bolt 53 is positioned to straddle the first carrier 31 and the second carrier 32.

[0067] A counterbore 55 is formed in the fitting hole 54 at the second end 32b of the second carrier 32 on the second direction side. The head 53c of the reamer bolt 53 is inserted into the counterbore 55. This reduces the protrusion height of the head 53c of the reamer bolt 53 from the second end 32b of the second carrier 32.

[0068] The outer circumferential surface 32c of the second carrier 32 has a reduced diameter portion 56 formed in most of the axial center via a stepped portion 56a. The inner race 13b of the second bearing 13 is fitted into this reduced diameter portion 56. As a result, the second carrier 32 is rotatably supported by the second housing 8 via the second bearing 13.

[0069] A second labyrinth section 57 on the second carrier side is formed on the first direction side of the location where the second bearing 13 is fitted in the reduced diameter section 56. The second labyrinth section 57 on the second carrier side is formed by making its outer diameter smaller than the outer diameter of the reduced diameter section 56 via a stepped section 57a. The outer diameter of the second labyrinth section 57 on the second carrier side is slightly smaller than the inner diameter of the first labyrinth section 25 on the second carrier side of the second housing 8.

[0070] The tip of the second labyrinth section 57 on the second carrier side is located slightly in front of the stepped section 25a of the first labyrinth section 25 on the second carrier side. In this way, the second labyrinth 40 is formed by the first labyrinth section 25 on the second carrier side of the second housing 8 and the second labyrinth section 57 on the second carrier side of the second carrier 32.

[0071] Slightly radially inward from the second labyrinth portion 57 on the second carrier side of the second carrier 32, a plurality of shaft support holes 58 (for example, three in this embodiment) are formed at equal intervals in the circumferential direction. The shaft support holes 58 rotatably support the crankshaft (eccentric rotating body) 4. These shaft support holes 58 and the corresponding shaft support recesses 44 of the first carrier 31 are located coaxially. A second bearing 59b is fitted into the shaft support hole 58. The second bearing 59b is, for example, a sliding bearing. However, it is not limited to this, and various bearings such as ball bearings can be used.

[0072] <crankshaft> Each crankshaft 4 is rotatably supported in the shaft support recess 44 and shaft support hole 58 via bearings 59a and 59b. The crankshaft 4 can be said to be slidably rotated in the shaft support recess 44 and shaft support hole 58 via bearings 59a and 59b. In this embodiment, there are three crankshafts 4. Each crankshaft 4 is integrally molded with bearing portions 4a and 4b (first bearing portion 4a and second bearing portion 4b) which are rotatably supported in a shaft support recess 44 and a shaft support hole 58 via bearings 59a and 59b, and a cylindrical eccentric portion 4c provided between each bearing portion 4a and 4b.

[0073] The rotation axis of the crankshaft 4 (second axis C2), that is, the axes of each bearing section 4a, 4b, are parallel to the first axis C1. The axial movement of the crankshaft 4 is restricted by thrust bearings 61a, 61b (first thrust bearing 61a, second thrust bearing 61b) provided on the axially outer side of each bearing section 4a, 4b, a first collar 70a provided in the shaft support recess 44 of the first carrier 31, and a second collar 70b provided in the shaft support hole 58 of the second carrier 32. Of the two thrust bearings 61a, 61b, the second thrust bearing 61b provided in the shaft support hole 58 of the second carrier 32 is restricted from moving in the second direction by a retaining ring 62 provided in the shaft support hole 58.

[0074] The axial length of the eccentric portion 4c is formed to fit within the axial width of the oscillating gear housing 60. Specifically, the axial length of the eccentric portion 4c is slightly shorter than the axial length of the thickened portion 10 of the first housing 7. Therefore, the position of the end of the eccentric portion 4c in the second direction and the position of the first end 8b of the second housing 8 are approximately on the same plane. The axis of the eccentric portion 4c (third axis C3) is eccentric with respect to the second axis C2 of the crankshaft 4. The oscillating gear 5 is rotatably supported in this eccentric portion 4c via a third bearing 59c. The third bearing 59c is, for example, a sliding bearing. However, it is not limited to this, and various bearings such as ball bearings can be used.

[0075] The outer diameter of the oscillating gear 5 is smaller than the diameter of the inner circumferential surface 10d of the thickened portion 10 so that it can be housed in the oscillating gear housing 60. The axial thickness of the oscillating gear 5 is equivalent to that of the eccentric portion 4c. Therefore, the position of the end of the oscillating gear 5 in the second direction and the position of the first end 8b of the second housing 8 are on approximately the same plane. The oscillating gear 5 has a support hole 63 formed at a position corresponding to the crankshaft 4, through which the eccentric portion 4c of the crankshaft 4 passes.

[0076] Each support hole 63 is arranged at equal intervals in the circumferential direction. A third bearing 59c is provided in these support holes 63. The axial movement of the oscillating gear 5 relative to the crankshaft 4 is restricted by retaining rings 67 provided at both axial ends of the third bearing 59c. Under this configuration, the rotation of the oscillating gear 5 is restricted to oscillating rotation by the crankshaft 4.

[0077] Furthermore, the oscillating gear 5 has relief holes 64 formed in positions corresponding to the support columns 34 of the first carrier 31, through which the support columns 34 pass. The shape of the relief holes 64 when viewed from the axial direction is triangular, corresponding to the shape of the support columns 34 when viewed from the axial direction. The size of the relief holes 64 is made sufficiently larger than the outer surface shape of each support column 34 so that the support columns 34 do not obstruct the oscillating rotational movement of the oscillating gear 5.

[0078] The outer circumferential surface of the oscillating gear 5 faces the internal tooth pin 90 of the first housing 7 in the radial direction. External teeth 65 that mesh with the internal tooth pin 90 are formed on the outer circumferential surface of the oscillating gear 5. The number of teeth of the external teeth 65 is different from the number of teeth (number) of the internal tooth pin 90. For example, in this embodiment, the number of teeth of the external teeth 65 is 12, which is one less than the number of teeth of the internal tooth pin 90. This number matches the number of supply passages 41 and discharge passages 42 formed in the first carrier 31.

[0079] During the oscillating rotational motion, the oscillating gear 5 always has contact with the internal tooth pin 90 at some point between the tooth tip 65a and the tooth root 65b. As a result, two large working chambers 66a and 66b (first working chamber 66a and second working chamber 66b) are formed between the inner circumferential surface 10d of the thickened portion 10 formed in the first housing 7 and the external teeth 65 of the oscillating gear 5. The two working chambers 66a and 66b are formed symmetrically when viewed from the axial direction.

[0080] Multiple through-holes (supply and discharge ports) 46a of the supply and discharge plate (port plate) 46 pass through these working chambers 66a and 66b. Hydraulic fluid is supplied to the working chambers 66a and 66b, and hydraulic fluid is discharged from the working chambers 66a and 66b through these through-holes 46a. This causes the hydraulic motor 1 to rotate.

[0081] <Brake mechanism> Figure 5 is an enlarged view of section V in Figure 1, showing the brake mechanism 100 in the released state. Figure 6 is an enlarged view of section V in Figure 1, showing the brake mechanism 100 in the engaged state. The hydraulic motor 1 is equipped with a brake mechanism 100 that acts as its parking brake. The parking brake is released when the hydraulic motor 1 is driven and stops when it is pulled. The brake mechanism 100 includes a stopper engaging portion 101, a stopper 102, a piston 103, a cylinder 104, a spring 105, and a branched passage 41g.

[0082] The stopper engaging portion 101 is formed to penetrate the oscillating gear 5 at its central position. The stopper engaging portion 101 has an axis C5 parallel to the first axis C1. The stopper engaging portion 101 moves around the first axis C1 in accordance with the oscillation of the oscillating gear 5, but in Figure 5 it is shown as axis C5.

[0083] A cylinder 104 is formed on the base plate portion 33 facing the stopper engagement portion 101 on the first direction side, with an opening at the second end portion 33b. A piston 103 is housed inside the cylinder 104. The cylinder 104 has an axis C5 parallel to the first axis C1. The piston 103 is capable of reciprocating movement inside the cylinder 104 along axis C5, which is in the direction of axis C1.

[0084] A spring (compression part) 105 is positioned inside the cylinder 104 on the first direction side of the piston 103. The spring (compression part) 105 presses the piston 103 in a second direction. Inside the cylinder 104, a branch passage 41g is connected to a position on the second direction side of the piston 103. The branch passage 41g is connected to the pressure chamber 104a of the cylinder 104 on the second direction side of the piston 103. The branch passage 41g branches off from the supply passage 41.

[0085] The branch channel 41g can supply the hydraulic fluid (working fluid) diverted from the supply channel 41 to the pressure chamber 104a. In the pressure chamber 104a, where the hydraulic fluid (working fluid) is supplied, the piston 103 is pressed in the first direction. When the pressure on the piston 103 from the hydraulic fluid (working fluid) in the pressure chamber 104a becomes greater than the pressing force of the spring (pressing part) 105, the piston 103 moves in the first direction.

[0086] When the pressure exerted on the piston 103 by the hydraulic fluid in the pressure chamber 104a is less than the pressing force of the spring (pressing part) 105, and when hydraulic fluid is supplied to the pressure chamber 104a, the piston 103 can move in the second direction due to the pressing force of the spring (pressing part) 105.

[0087] The second directional end of the piston 103 is formed as a stopper 102, with the same diameter as the stopper engagement portion 101. The stopper 102 and the stopper engagement portion 101 have the same cross-sectional shape. The stopper 102 and the stopper engagement portion 101 can have a circular cross-section or a polygonal cross-section.

[0088] The stopper 102 moves along axis C5 so as to be able to contact and separate from the oscillating gear 5 in accordance with the reciprocating motion of the piston 103. The stopper 102 can protrude in a second direction from the second end 33b of the base plate 33 by the pressing force of the spring (pressing part) 105. When the stopper 102 moves in the second direction, the stopper 102 is inserted into the stopper engaging part 101. At this time, depending on the oscillating rotation position of the oscillating gear 5, the positions of the stopper 102 and the stopper engaging part 101 may not match, but during one rotation of the output rotation of the carrier part 6, the positions of the stopper 102 and the stopper engaging part 101 will always coincide. When the positions of the stopper 102 and the stopper engaging part 101 coincide, the stopper 102 is inserted into the stopper engaging part 101. When the stopper 102 is inserted into the stopper engagement portion 101, the stopper 102 stops the oscillating rotation of the oscillating gear 5.

[0089] The stopper 102, which is inserted into the stopper engagement portion 101 by the pressing force of the spring (pressing portion) 105, overcomes the pressing force of the spring 105 and pushes the piston 103 in the first direction when hydraulic fluid is supplied to the pressure chamber 104a via the branched passage 41g. As the piston 103 moves in the first direction, the stopper 102 moves in the first direction and disengages from the stopper engagement portion 101. Furthermore, the stopper 102, which is separated from the oscillating gear 5, is located in the first direction from the second end 33b of the base portion 33 and is housed inside the cylinder 104.

[0090] The spring (pressing part) 105, the piston 103 and cylinder 104 which are the release parts, and the branching passage 41g constitute the stopper moving part 100a.

[0091] <Operation of hydraulic motor> The operation of hydraulic motor 1 will be described in detail below.

[0092] The hydraulic motor 1 receives hydraulic fluid supplied from a hydraulic pump (not shown) via an oil distribution unit 45 to each supply passage 41. The hydraulic fluid supplied to each supply passage 41 is then supplied to the working chambers 66a and 66b via the piston 51 of each supply opening 41a, the through-hole (through-port) 50c of the sliding plate (piston plate) 50, and the through-hole (supply / discharge port) 46a of the supply / discharge plate (port plate) 46.

[0093] Here, the piston 51 of each supply opening 41a slides against the sliding plate 50, which rotates integrally with the first carrier 31, while being pressed toward the sliding plate 50 by a spring. When the through hole (through port) 50c comes to a position aligned with the piston 51 due to the rotation of the sliding plate 50, the hydraulic fluid supplied to the supply passage 41 flows into the through hole (through port) 50c.

[0094] The sliding plate (piston plate) 50, which rotates integrally with the first carrier 31, slides against the supply / discharge plate (port plate) 46, which is integrated with the housing 2. When the through hole (supply / discharge port) 46a comes to a position that coincides with the through hole (through port) 50c due to the rotation of the sliding plate 50 and the supply / discharge plate 46, the hydraulic fluid supplied to the through hole (through port) 50c flows into the through hole (supply / discharge port) 46a. Furthermore, if the through-hole (supply / discharge port) 46a and the through-hole (supply / discharge port) 50c do not coincide and communicate, the sliding plate (piston plate) 50 blocks the through-hole (supply / discharge port) 46a, preventing hydraulic fluid from leaking or backflowing from the working chambers 66a and 66b through the through-hole (supply / discharge port) 46a.

[0095] Here, the number of supply passages 41 (supply opening 41a and through-holes 50c in the sliding plate 50 leading to the supply opening 41a) is one less than the number of through-holes 46a in the supply and discharge plate 46. Also, the number of discharge passages 42 (discharge opening 42a and through-holes 50c in the sliding plate 50 leading to the discharge opening 42a) is one less than the number of through-holes 46a in the supply and discharge plate 46. Therefore, only the supply passage 41 is accessible through the through-holes 46a in the supply and discharge plate 46 to one of the two working chambers 66a and 66b. Also, only the discharge passage 42 is accessible through the through-holes 46a in the supply and discharge plate 46 to the other of the two working chambers 66a and 66b.

[0096] As a result, the pressure inside one of the two working chambers 66a and 66b becomes higher than the pressure inside the other working chamber 66a or 66b. To make the explanation easier to understand, we will now describe the case where the pressure in working chamber 66a (left side in Figure 2) is higher than the pressure in working chamber 66b (right side in Figure 2). In the following explanation, the working chamber 66a with higher pressure will be referred to as the high-pressure working chamber 66a. The working chamber 66b with lower pressure compared to the high-pressure working chamber 66a will be referred to as the low-pressure working chamber 66b. The high-pressure working chamber 66a is connected to the supply passage 41. The low-pressure working chamber 66b is connected to the discharge passage 42.

[0097] When hydraulic fluid is supplied to the high-pressure working chamber 66a, the oscillating gear 5 is pressed toward the low-pressure working chamber 66b (see arrow Y1 in Figure 2). The hydraulic fluid in the low-pressure working chamber 66b is discharged through the discharge passage 42. As a result, the internal tooth pin 90 and the external teeth 65 of the oscillating gear 5 mesh on the low-pressure working chamber 66b side. Then, because the number of teeth on the external teeth 65 is one less than the number of teeth on the internal tooth pin 90, the oscillating gear 5 is slightly displaced in the rotational direction.

[0098] At this time, the carrier section 6 is pulled in the rotational direction by the oscillating gear 5 via the crankshaft 4. That is, the rotating section 3 is rotated slightly relative to the housing section 2. As a result, the sliding plate 50 is rotated relative to the supply and discharge plate 46. Then, the state in which the through hole 50c of the sliding plate 50 and the through hole 46a of the supply and discharge plate 46 are connected is switched. As the oscillating gear 5 is rotated, the high-pressure working chamber 66a is also pulled slightly in the rotational direction relative to the low-pressure working chamber 66b.

[0099] When the connection between the through-hole 50c of the sliding plate 50 and the through-hole 46a of the supply / discharge plate 46 is reversed, hydraulic fluid is supplied again to the high-pressure working chamber 66a. At the same time, hydraulic fluid is discharged from the low-pressure working chamber 66b. By repeating this process sequentially, the rotating part 3 is rotated relative to the housing part 2. Output is obtained through this rotation.

[0100] Here, when the through-hole (supply / discharge port) 46a comes to a position that coincides with the through-hole (through-port) 50c due to the rotation of the sliding plate 50 and the supply / discharge plate 46, hydraulic fluid is discharged from the low-pressure working chamber 66b into the through-hole (through-port) 50c. Furthermore, if the through-hole (supply / discharge port) 46a and the through-hole (supply / discharge port) 50c do not coincide and communicate, the sliding plate (piston plate) 50 blocks the through-hole (supply / discharge port) 46a, preventing hydraulic fluid from being discharged from the working chambers 66a and 66b through the through-hole (supply / discharge port) 46a.

[0101] The piston 51 at the discharge opening 42a of the discharge passage 42 slides against the sliding plate (piston plate) 50, which rotates integrally with the first carrier 31, while being pressed toward the sliding plate 50 by a spring. When the through hole (through port) 50c comes to a position aligned with the piston 51 due to the rotation of the sliding plate 50, the hydraulic fluid discharged from the through hole (supply / discharge port) 46a is discharged into the discharge passage 42 via the piston 51 at the discharge opening 42a. The hydraulic fluid discharged into the discharge passage 42 is returned to the tank via the distribution channel.

[0102] In this way, the hydraulic motor 1 utilizes the mismatch between the number of supply passages 41 (supply opening 41a and through holes 50c in the sliding plate 50 leading to the supply opening 41a) and the number of through holes 46a in the supply / discharge plate 46, and the mismatch between the number of discharge passages 42 (discharge opening 42a and through holes 50c in the sliding plate 50 leading to the discharge opening 42a) and the number of through holes 46a in the supply / discharge plate 46, so that the state in which the through holes 50c in the sliding plate 50 and the through holes 46a in the supply / discharge plate 46 are connected is sequentially switched in the circumferential direction. As a result, hydraulic fluid is selectively supplied and discharged from each through hole 46a in the supply / discharge plate 46 to each working chamber 66a, 66b, and the rotating part 3 is rotated.

[0103] The carrier section 6, which constitutes the rotating section 3, is divided into a first carrier 31 and a second carrier 32. Since the first carrier 31 and the second carrier 32 are fixed together by a reamer bolt 53, power is transmitted between the first carrier 31 and the second carrier 32 via this reamer bolt 53. The shaft portion 53a of the reamer bolt 53 is positioned across the first carrier 31 and the second carrier 32. Therefore, compared to the case where the male threaded portion 53b spans between the first carrier 31 and the second carrier 32, power is transmitted between the first carrier 31 and the second carrier 32 more efficiently.

[0104] Here, on the first direction side of the oscillating gear 5, a third labyrinth 49 is formed by the first outer peripheral surface 33d of the first carrier 31, the second end portion 33b, and the plate-side labyrinth portion 48 of the supply / discharge plate 46. On the second direction side of the oscillating gear 5, a second labyrinth 40 is formed by the second carrier-side first labyrinth portion 25 of the second housing 8 and the second carrier-side second labyrinth portion 57 of the second carrier 32. As a result, hydraulic fluid leaking from the working chambers 66a, 66b through the minute gap between the crankshaft 4 and the oscillating gear 5 is less likely to leak from between the first housing 7 and the first carrier 31, and from between the second housing 8 and the second carrier 32.

[0105] In the hydraulic motor 1, output can be obtained from the rotating part 3 by fixing the housing part 2. In this case, the external device fixed to the outer flange part 39 of the rotating part 3 (first carrier 31) becomes the rotating object. Alternatively, output can be obtained from the housing part 2 by fixing the rotating part 3. In this case, the external device fixed to the outer flange part 9 of the housing part 2 (first housing 7) becomes the rotating object.

[0106] The hydraulic motor 1 has an internal tooth pin 90 provided in the first housing 7. The rotating part 3 includes a carrier part 6, a crankshaft 4 rotatably supported by the carrier part 6, and an oscillating gear 5 that is driven to oscillate by the crankshaft 4 and meshes with the internal tooth pin 90. With this configuration, the hydraulic motor 1 can be rotationally driven by supplying and discharging hydraulic fluid into the working chambers 66a and 66b formed between the inner circumferential surface 7c of the first housing 7 and the outer circumferential surface of the oscillating gear 5. This rotational drive can provide high rotational torque. The divided housing part 2 can be suitably used in such a hydraulic motor 1.

[0107] The hydraulic motor 1 has a supply and discharge plate 46 for selectively supplying and discharging hydraulic fluid to and from each working chamber 66a, 66b. The supply and discharge plate 46 is located at the first end 10b of the thickened portion 10 (the first direction side end of the oscillating gear 5). This supply and discharge plate 46 is fixed to the first housing 7 using bolts 20. The supply and discharge plate 46 is also fixed using the bolts 20 that fix the first housing 7 and the second housing 8 together.

[0108] In the hydraulic motor 1, when selectively supplying hydraulic fluid to the working chambers 66a and 66b, the fluid is branched from the branching passage 41g and supplied to the pressure chamber 104a.

[0109] When hydraulic fluid is not supplied from the hydraulic pump, no hydraulic fluid is supplied to the pressure chamber 104a. Therefore, in the brake mechanism 100, the piston is pressed in the second direction by the pressing force of the (pressing part) 105. In this state, as shown in Figure 6, the stopper 102 is inserted into the stopper engaging part 101, and the oscillating gear 5 does not oscillate. Therefore, the hydraulic motor 1 does not drive. In other words, the brake is maintained in an applied state. In this state, the brake mechanism 100 becomes a parking brake.

[0110] In this state, when hydraulic fluid is supplied to the pressure chamber 104a, the hydraulic fluid in the pressure chamber 104a overcomes the pressing force of the (pressing part) 105, and the piston 103 moves in the first direction. Then, as shown in Figure 5, the stopper 102 disengages from the stopper engagement part 101, and the restriction on the oscillating gear 5 is released. As a result, the oscillating gear 5 becomes able to oscillate, and the hydraulic motor 1 is driven.

[0111] The hydraulic fluid may be supplied to the pressure chamber 104a from the hydraulic pump that drives the hydraulic motor 1 that supplies hydraulic fluid to the working chambers 66a and 66b, or it may be supplied by another pilot pressure.

[0112] As described above, in the embodiment described, the brake mechanism 100 can be operated as a parking brake by the spring (pressing part) 105 and the stopper moving part 100a which uses the hydraulic fluid used to drive the hydraulic motor 1. This makes it possible to configure the crankshaft 4 and the stopper 102 as separate components in a so-called orbit-type hydraulic motor 1 using an oscillating gear, preventing them from rotating together or performing integrated operations. This reduces the resistance to driving the hydraulic motor 1 and reduces energy loss. Moreover, this effect can be provided inexpensively with a simple structure in which the stopper 102, which reciprocates using a cylinder 104, piston 103, and spring 105 provided on the base plate 33, moves back and forth against the stopper engaging part 101 provided on the oscillating gear 5.

[0113] Furthermore, the stopper 102, driven by a cylinder 104, piston 103, and spring 105 provided on the base plate 33, can be moved back and forth on a stopper engagement portion 101 provided on the oscillating gear 5, resulting in a compact and simple structure. Because of the simple structure of moving back and forth on a stopper engagement portion 101 provided on the oscillating gear 5, it is easy to manufacture. Since the cylinder 104 and piston 103 are provided on the base plate 33, it is easy to form a branch passage 104g for supplying hydraulic fluid to release the brake. Also, since the base plate 33 is a non-rotating part, a passage can be easily formed. Furthermore, since only one branch passage 41g is formed to supply hydraulic fluid for brake drive to the cylinder 104, space can be saved.

[0114] Furthermore, the arrangement of the crankshaft 4, cylinder 104, and piston 103 can be easily performed. In addition, by making the brake function simply by inserting the stopper 102 into the stopper engagement portion 101, it can be operated without worrying about the inclination between the stopper 102 and the stopper engagement portion 101. This makes it possible to achieve reliable braking operation while reducing the number of parts.

[0115] A second embodiment of the rotating device according to the present invention will be described below with reference to the drawings. Figure 7 corresponds to an enlarged view of section V in Figure 1 and shows the released state of the brake mechanism 100 in this embodiment. Figure 8 corresponds to an enlarged view of section V in Figure 1 and shows the engaged state of the brake mechanism 100. In this embodiment, the difference from the first embodiment described above is in the part relating to the stopper moving part, and other components corresponding to the first embodiment described above are denoted by the same reference numerals and their descriptions are omitted.

[0116] In this embodiment, the stopper moving part 100a has a cylinder 106 formed on the second carrier 32, as shown in Figure 7. The cylinder 106 has an opening in its first direction facing the oscillating gear 5. The cylinder 106 has a communication opening in its second direction facing the cover 29. Inside the cylinder 106, the stopper 102 is housed on the first direction side. The cylinder 106 may have the same diameter as the cylinder 104. The cylinder 104 has the same axis C5 as the cylinder 104 and is formed coaxially with the cylinder 104. The stopper 102 is reciprocating inside the cylinder 106 along axis C5, which is in the direction along axis C1.

[0117] A spring (pressing part) 105 is positioned inside the cylinder 106 on the second direction side of the stopper 102. The spring (pressing part) 105 presses the stopper 102 toward the first direction. A connecting member 102a is connected to the stopper 102 on the first direction side, along the axis C5. The connecting member 102a is connected coaxially with respect to the axis C5 of the stopper 102. A piston 103 is connected to the end of the connecting member 102a on the first direction side. The stopper 102, the connecting member 102a, and the piston 103 are all movable together in the direction along the axis C5. The connecting member 102a is positioned inside the stopper engagement portion 101. The connecting member 102a has a smaller diameter than the stopper engagement portion 101, so that it does not come into contact with the stopper engagement portion 101 even when the oscillating gear 5 oscillates.

[0118] The piston 103 is housed in the cylinder 104. Cylinders 104 and 106 are arranged coaxially on both sides of the oscillating gear 5 in the thickness direction. Cylinder 104 on the first direction side of the oscillating gear 5 and cylinder 106 on the second direction side of the oscillating gear 5 are formed as if they were continuous cylinders in the direction of axis C5. In other words, cylinders 104 and 106 are formed in the carrier section 6. Inside cylinder 104, a branch passage 41g is connected at a position on the first direction side of piston 103. The branch passage 41g is connected to the pressure chamber 104b of cylinder 104 on the first direction side of piston 103. The branch passage 41g branches off from supply passage 41.

[0119] The branch channel 41g can supply the hydraulic fluid (working fluid) diverted from the supply channel 41 to the pressure chamber 104b. In the pressure chamber 104b, where the hydraulic fluid (working fluid) is supplied, the piston 103 is pressed in the second direction. When the pressure on the piston 103 from the hydraulic fluid (working fluid) in the pressure chamber 104b becomes greater than the pressing force exerted by the spring (pressing part) 105 of the cylinder 106 on the stopper 102 in the first direction, the piston 103 and the stopper 102 move in the second direction.

[0120] The stopper 102 moves along the axis C5, integrally with the connecting member 102a and the piston 103, so as to be able to contact and separate from the oscillating gear 5. The stopper 102 can protrude in the first direction from the first direction end 32d of the second carrier 32 by the pressing force of the spring (pressing part) 105. When the stopper 102 moves in the first direction, the stopper 102 is inserted into the stopper engaging part 101. At this time, depending on the oscillating rotation position of the oscillating gear 5, the positions of the stopper 102 and the stopper engaging part 101 may not match, but during one rotation of the output rotation of the carrier part 6, the positions of the stopper 102 and the stopper engaging part 101 will always coincide. When the positions of the stopper 102 and the stopper engaging part 101 coincide, the stopper 102 is inserted into the stopper engaging part 101. When the stopper 102 is inserted into the stopper engagement portion 101, the stopper 102 stops the oscillating rotation of the oscillating gear 5.

[0121] The stopper 102, which is inserted into the stopper engagement portion 101 by the pressing force of the spring (pressing portion) 105, overcomes the pressing force of the spring 105 and pushes the piston 103 in the second direction when hydraulic fluid is supplied to the pressure chamber 104b via the branched passage 41g. As the piston 103 moves in the second direction, the integrated stopper 102 moves in the second direction via the connecting member 102a and disengages from the stopper engagement portion 101. Furthermore, the stopper 102, which is separated from the oscillating gear 5, is located in the second direction beyond the first direction end 32d of the second carrier 32 and is housed inside the cylinder 106.

[0122] In this embodiment as well, hydraulic fluid is supplied to the hydraulic motor 1 from a hydraulic pump (not shown) via a supply passage 41 into the working chambers 66a and 66b. As a result, the hydraulic fluid supplied to the working chambers 66a and 66b causes the oscillating gear 5 to shift slightly in the rotational direction, thereby generating rotational output. Simultaneously, the hydraulic fluid is supplied from the supply passage 41 to the pressure chamber 104b via a branch passage 41g.

[0123] When hydraulic fluid is not supplied from the hydraulic pump, no hydraulic fluid is supplied to the pressure chamber 104b. Therefore, in the brake mechanism 100, the piston is pressed in the first direction by the pressing force of the (pressing part) 105. In this state, as shown in Figure 8, the stopper 102 is inserted into the stopper engaging part 101, and the oscillating gear 5 does not oscillate. Therefore, the hydraulic motor 1 does not drive. In other words, the brake is maintained in an applied state. In this state, the brake mechanism 100 becomes a parking brake.

[0124] In this state, when hydraulic fluid is supplied to the pressure chamber 104b, the pressure of the hydraulic fluid in the pressure chamber 104b overcomes the pressing force of the (pressing part) 105, and the piston 103 moves in the second direction, as shown in Figure 7. Then, the stopper 102, which has been moved via the connecting member 102a, disengages from the stopper engagement part 101, and the restriction on the oscillating gear 5 is released. As a result, the oscillating gear 5 becomes able to oscillate, and the hydraulic motor 1 is driven.

[0125] The hydraulic fluid may be supplied to the pressure chamber 104b from the hydraulic pump that drives the hydraulic motor 1 that supplies hydraulic fluid to the working chambers 66a and 66b, or it may be supplied by another pilot pressure.

[0126] In this embodiment as well, the brake mechanism 100 can be operated as a parking brake by the spring (pressing part) 105 and the stopper moving part 100a which uses the hydraulic fluid used to drive the hydraulic motor 1. This makes it possible to achieve the same effect as described above. Furthermore, since the cylinder 106 is formed on the second carrier 32, there is no need to create space for housing the spring 105 in the cylinder 104 of the base plate portion 33. At the same time, there is no need to form the pressure chamber 104a on the second side of the piston 103. For these reasons, space can be saved in the base plate portion 33.

[0127] In each of the embodiments described above, the rotation of the oscillating gear 5 is stopped by the stopper 102. However, the braking mechanism 100 can also be configured to stop the rotation of the crankshaft 4. In this case, it is preferable that the crankshaft 4 is located at the center of the oscillating gear 5. Furthermore, in each of the above embodiments, the stopper engagement portion 101 is formed to penetrate the oscillating gear 5, but it can also be formed as a recess into which the stopper 102 engages, and not penetrate the gear 5. Alternatively, the stopper 102 can be configured to contact the oscillating gear 5 or the crankshaft 4 and press against them to stop their rotation.

[0128] Among the embodiments disclosed herein, those composed of multiple objects may be integrated, and conversely, those composed of a single object may be divided into multiple objects. Whether or not they are integrated, the invention can be constructed in a way that achieves its objective. [Explanation of Symbols]

[0129] 1… Hydraulic motor (rotating equipment) 2…Housing Department 3…Rotating part 4…Crankshaft (eccentric rotating body) 4c...Eccentric part 5... Oscillating gear 6…Carrier section (rotating member) 7…1st Housing 8…Second Housing 12…First bearing (bearing) 13…Second bearing (bearing) 31…First Career 33b…Second end 32…Second career (career) 32d…first direction end 41…Supply channel (oil channel) 41g…Branching channel 42...Discharge path (oil path) 46…Intake / exhaust plate (port plate) 50... Sliding plate (piston plate) 65…External teeth 66a, 66b…Operating chambers 90...Inner tooth pin (inner tooth) 100... Brake mechanism 100a... Stopper movement part 101... Stopper engagement part 102... Stopper 102a... Connecting member 103... Piston 104, 106… cylinders 104a, 104b… Pressure chambers 105... Spring (pressure part) C1…1st axis line (axis line) C5…Axis line

Claims

1. A housing section having an axis, The internal teeth provided on the inner circumferential surface of the housing portion, A carrier portion is supported in the housing portion so as to be rotatable around the axis, A crankshaft is supported in the carrier portion so as to be rotatable around another axis parallel to the aforementioned axis, A rocking gear whose rotation is restricted by the crankshaft and which meshes with the internal teeth, Multiple supply and discharge channels are provided to supply working fluid between the inner circumferential surface of the housing and the oscillating gear and to discharge working fluid from between the inner circumferential surface of the housing and the oscillating gear. A stopper that can move so as to be able to contact and separate from either the oscillating gear or the crankshaft, The stopper moving part presses or releases the stopper toward the oscillating gear so that the stopper can move toward and away from the oscillating gear or the crankshaft, Equipped with, Rotating machinery.

2. The stopper holds down the oscillating gear and stops its oscillating rotation. The rotating apparatus according to claim 1.

3. The stopper moving part moves the stopper along the rotation axis direction of the oscillating gear. The rotating apparatus according to claim 1 or 2.

4. The crankshafts are arranged in the circumferential direction around the axis, The stopper is located near the center of the oscillating gear. The rotating apparatus according to claim 1 or 2.

5. The stopper is supported by the carrier portion. The rotating apparatus according to claim 1 or 2.

6. An eccentric stopper engagement portion is formed on the oscillating gear, and the stopper movement portion inserts the stopper into the stopper engagement portion to stop the oscillating rotation. The rotating apparatus according to claim 1 or 2.

7. The stopper movement part is, A pressing portion that presses against the stopper and inserts into the stopper engagement portion to stop the oscillating rotation of the oscillating gear, A release unit that releases the pressing state of the pressing portion against the stopper using a working fluid and removes the stopper from the stopper engagement portion, Equipped with, The rotating device according to claim 6.

8. Two bearings are provided spaced apart from each other along the axis of the housing portion to support the carrier portion relative to the housing portion, A supply and discharge plate is positioned adjacent to the oscillating gear along the axial direction, having a plurality of supply and discharge channels for supplying working fluid to an operating chamber formed between the inner circumferential surface of the housing and the oscillating gear, and for discharging working fluid from the operating chamber formed between the inner circumferential surface of the housing and the oscillating gear, The carrier portion is formed and each of the multiple supply and discharge passages leads to the outside, and the branch passage is branched from the fluid supply passage to the working chamber and leads to the release section. Equipped with, The working fluid supplied to the release section via the branched channel releases the pressing force of the pressing section against the stopper. The rotating apparatus according to claim 7.

9. A housing section having an axis, The internal teeth provided on the inner circumferential surface of the housing portion, A carrier portion is supported in the housing portion so as to be rotatable around the axis, via two bearings provided spaced apart from each other along the axis of the housing portion. The carrier portion is rotatably supported around another axis parallel to the aforementioned axis, and the crankshafts are arranged in the circumferential direction around the aforementioned axis, A rocking gear whose rotation is restricted by the crankshaft and which meshes with the internal teeth, A supply and discharge plate is positioned adjacent to the oscillating gear along the axial direction, having a plurality of supply and discharge channels for supplying working fluid to an operating chamber formed between the inner circumferential surface of the housing and the oscillating gear, and for discharging working fluid from the operating chamber formed between the inner circumferential surface of the housing and the oscillating gear, A stopper supported by the carrier portion and located near the center of the oscillating gear, which can move to contact and separate from the oscillating gear, A stopper engaging portion formed eccentrically on the aforementioned oscillating gear, The stopper is moved so as to be able to contact and separate from the stopper engagement portion of the oscillating gear, by a stopper moving portion that presses the stopper toward or releases the stopper from the stopper engagement portion, The carrier portion is formed and each of the multiple supply and discharge channels leads to the outside, Of the aforementioned flow paths, a branch flow path is branched from the fluid supply path to the working chamber and leads to the stopper moving section, Equipped with, The stopper movement part is, A pressing portion that presses against the stopper and inserts into the stopper engagement portion to stop the oscillating rotation of the oscillating gear, A release unit that releases the pressing state of the pressing portion against the stopper by using the working fluid supplied through the branched passage to remove the stopper from the stopper engagement portion, Having, Rotating machinery.

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