CN116181560A - rotating equipment - Google Patents

Abstract

The invention relates to rotating equipment. The rotary device of the present invention includes a housing portion, internal teeth, a carrier portion, a crankshaft, a swing gear, a plurality of supply and discharge channels, a stopper, and a stopper moving portion.

Description

rotating equipment

technical field

The invention relates to a rotating device.

Background technique

Conventionally, hydraulic pumps and motors described in Patent Documents 1 and 2 are known. In this document, a hydraulic pump and a motor are used as a parking brake that stops the movement by restricting the swing of the swing member. As a structure of the parking brake, for example, Patent Document 1 describes a structure in which the brake pin 60 in the locked position in which the swing of the star gear 30 is suppressed is moved to the unlocked position by the brake lever 72 to release the lock. .

There has previously been a technique of placing the restricting shaft in the center hole of the swing gear in this way. So far, the method of moving the restricting shaft and the oil passage have been improved.

prior art literature

patent documents

Patent Document 1: Japanese Patent No. 5822512

Patent Document 2: Japanese Patent No. 5288184

Contents of the invention

The problem to be solved by the invention

In the technique described in the patent document, the central spline shaft is hollow, and a shaft for transmitting force to the restricting shaft is provided therein. Therefore, the structure is relatively complicated. Therefore, there is a problem that the manufacturing process becomes complicated.

In addition, it is a structure in which the restriction shaft precesses following the precession of the central spline shaft, so the end face is worn. Therefore, there is a problem that the durability is lowered.

The present invention provides a rotary device having a parking brake function with a simple structure, high durability, and miniaturization.

solutions to problems

A rotary device according to an aspect of the present invention includes: a housing portion having an axis; internal teeth provided on an inner peripheral surface of the housing portion; the housing portion; the crankshaft, which is rotatably supported on the gear carrier portion around another axis parallel to the axis; the swing gear, which is restricted to swing and rotate by the crankshaft, and meshes with the internal teeth; a supply and discharge flow path for supplying working fluid between the inner peripheral surface of the housing part and the swing gear and discharging working fluid from between the inner peripheral surface of the housing part and the swing gear; a stopper a member that can move in a contactable and separable manner relative to any one of the swing gear and the crankshaft; and a stopper moving part that pushes the stopper toward the swing gear or releases Pressing so that the stopper can be moved toward the swing gear or the crankshaft in a contactable and separable manner. Thus, the above-mentioned problems are solved.

With such a configuration, the rotation of either the rocking gear or the crankshaft is stopped by the stopper, thereby stopping the drive of the rotary device. In this way, the stopper can be used as a stopper for the rotary device by driving the stopper with the stopper moving unit. Thus, it is possible to provide a rotary device having a simple and compact brake mechanism.

In the above configuration, the stopper may press the swing gear to stop the swing rotation.

In the above configuration, the stopper moving unit may move the stopper along the direction of the rotation axis of the swing gear.

In the above structure, the crankshafts may be arranged in a circumferential direction around the axis, and the stopper may be located near the center of the swing gear.

In the above configuration, the stopper may be supported by the carrier portion.

In the above configuration, an eccentric stopper engaging portion may be formed on the swing gear, and the stopper may be inserted into the stopper engaging portion by the stopper moving portion. Stop the swinging rotation.

In the above configuration, the stopper moving part may include a pressing part that pushes the stopper and inserts it into the stopper engaging part, so that the swing gear and a push release part that releases the push state of the stopper by the push part using working fluid, and pulls out the stopper from the stopper engaging part.

In the above configuration, the rotating device may include: two bearings provided separately from each other along the axis of the housing part, and supporting the gear frame part on the housing part; , which has the working fluid supplied to the working chamber formed between the inner peripheral surface of the housing part and the swing gear, and the working fluid from the working chamber formed between the inner peripheral surface of the housing part and the swing gear. A plurality of supply and discharge flow paths for discharging working fluid are arranged adjacent to the swing gear along the direction of the axis; the flow paths are formed in the gear frame portion so that the plurality of supply and discharge flow paths are respectively leading to the outside; and a branch flow path branching from a supply path for supplying working fluid to the working chamber in the flow path to lead to the pressing release portion. The pressing force of the pressing portion on the stopper may be released by the working fluid supplied to the pressing releasing portion via the branch flow path.

A rotary device according to another aspect of the present invention includes: a housing part having an axis; internal teeth provided on the inner peripheral surface of the housing part; Two bearings provided separately from each other are rotatably supported on the housing portion around the axis; a crankshaft is rotatably supported on the carrier portion around another axis parallel to the axis, and Arranged in the circumferential direction around the axis; a swing gear, which is restricted to swing and rotate by the crankshaft, meshes with the internal teeth; a supply and discharge plate, which has a direction on the inner peripheral surface of the housing part and the swing The working fluid is supplied to the working chamber formed between the gears, and a plurality of supply and discharge channels for discharging the working fluid from the working chamber formed between the inner peripheral surface of the housing part and the swing gear, along the axis The direction is arranged adjacent to the swing gear; the stopper, which is supported by the gear frame part, is located near the center of the swing gear, and moves in a contactable and separable manner relative to the swing gear; a stopper engaging portion formed eccentrically on the swing gear; a stopper moving portion that pushes or releases the stopper toward the stopper engaging portion so that the stopper The member moves toward the stopper engagement portion of the swing gear in a contactable and detachable manner; the flow path is formed on the gear frame portion, and a plurality of the supply and discharge flow paths lead to the outside, respectively. and a branch flow path branching from a supply path for supplying the working fluid to the working chamber among the flow paths to lead to the stopper moving portion. The stopper moving part has: a pressing part that presses the stopper to be inserted into the stopper engaging part to stop the swinging rotation of the swinging gear; and releases the push. and a part for releasing the pressing state of the stopper by the pressing part by the working fluid supplied through the branch flow path, so as to pull out the stopper from the stopper engaging part.

With this configuration, the stopper is inserted into the stopper engagement portion of the swing gear to stop the swing rotation of the swing gear, thereby stopping the drive of the rotary device. At this time, when the working fluid is supplied to the working chamber to drive the rotary device, the working fluid is supplied to the pressing release part of the stopper moving part through the branched flow path branched from the supply path, and the insertion of the working fluid in the stopper by the pressing part is released. The stopper of the stopper engaging part restricts the swing gear, and releases the position restriction of the swing gear. In this way, by driving the stopper by the stopper moving part, the stopper can be used as a parking brake that is released during driving and brakes during non-driving in rotating equipment. Thus, it is possible to provide a rotating machine having a simple and compact parking brake mechanism.

The effect of the invention

According to the present invention, there is an effect that a rotating machine having a parking brake function having a simple structure, high durability, and miniaturization can be provided.

Description of drawings

FIG. 1 is a side view showing a partial section of a hydraulic motor according to a first embodiment of the present invention.

Fig. 2 is a sectional view taken along line II-II of Fig. 1 .

Fig. 3 is an enlarged view of part III of Fig. 1 .

FIG. 4 is an enlarged view of part VI of FIG. 1 .

Fig. 5 is an enlarged view of a V portion showing a released state in Fig. 1 .

FIG. 6 is an enlarged view showing an engaged state in FIG. 5 .

7 is a view corresponding to a V portion in FIG. 1 of a hydraulic motor according to a second embodiment of the present invention, and is an enlarged view showing a released state.

Fig. 8 is an enlarged view showing the engaged state in Fig. 7 .

Explanation of reference signs

1. Hydraulic motor (rotating equipment); 2. Shell part; 3. Rotating part; 4. Crankshaft (eccentric rotating body); 4c. Eccentric part; 5. Swing gear; 6. Gear frame part (rotating member); 7. 1st shell; 8, the 2nd shell; 12, the 1st bearing (bearing); 13, the 2nd bearing (bearing); 31, the 1st gear frame; 33b, the 2nd end; 32, the 2nd gear frame (gear Frame); 32d, end of the first direction; 41, supply path (oil path); 41g, branch flow path; 42, discharge path (oil path); 46, supply and discharge plate (port plate); 50, sliding plate ( piston plate); 65, external teeth; 66a, 66b, working chamber; 90, inner tooth pin (internal teeth); 100, brake mechanism; 100a, stopper moving part; 101, stopper engaging part; 102 102a, connecting member; 103, piston; 104, 106, cylinder; 104a, 104b, pressure chamber; 105, spring (pressing part); C1, first axis (axis); C5, axis.

Detailed ways

Hereinafter, a rotating machine according to a first embodiment of the present invention will be described based on the drawings.

FIG. 1 is a partially cutaway side view showing a hydraulic motor as an example of rotating equipment in this embodiment. Fig. 2 is a sectional view taken along line II-II of Fig. 1 . Fig. 3 is an enlarged view of part III of Fig. 1 . Fig. 4 is an enlarged view of part IV of Fig. 1 . In the drawings, reference numeral 1 is a hydraulic motor.

First, a hydraulic motor will be described as a rotating machine according to the present embodiment.

＜Hydraulic motor＞

As shown in FIGS. 1 to 4 , a hydraulic motor 1 is rotatably supported by a cylindrical housing 2 via two bearings 12 and 13 (first bearing 12 and second bearing 13 ). The rotating part 3 on the inner peripheral surface and the braking mechanism 100 are the main structures.

Angular contact ball bearings are used as bearings 12 , 13 . However, the configuration of the bearings 12, 13 is not limited to angular contact ball bearings. Various bearings such as deep groove ball bearings and other ball bearings and sliding bearings can also be used for the bearings 12 and 13 .

The central axis of the housing part 2 coincides with the rotation axis of the rotating part 3 . In the following description, these center axes and rotation axes are collectively referred to as a 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 rotational direction of the rotating portion 3 may be referred to as the circumferential direction, and the radial direction of the rotating portion 3 may be simply referred to as the radial direction.

＜Shell part＞

The casing part 2 is divided in the axial direction, and consists of a first casing 7 arranged on the first direction side (left side in FIG. 1 ) in the axial direction and a first casing 7 arranged on the opposite side to the first direction in the axial direction. The second housing 8 on the 2-direction side (right side in FIG. 1 ) is constituted. In addition, the case part 2 may be set as the structure which is not divided|segmented in the axial direction.

The first housing 7 is formed in a cylindrical shape. On the outer peripheral surface 7 a of the first housing 7 , an outer flange portion 9 protruding radially outward is formed at a position closer to the first end portion 7 b on the first direction side. The outer flange portion 9 is used when attaching the hydraulic motor 1 to an unshown external device. Through-holes 9 a through which unillustrated bolts are inserted are formed in the outer flange portion 9 so as to penetrate in the thickness direction (axial direction) of the outer flange portion 9 .

A portion located between the second end portion 7d on the second direction side and the axial center of the peripheral wall 7e of the first housing 7 is a thick portion 10 thicker than other portions. The second end portion 10c on the second direction side of the thick portion 10 is located on the same plane as the second end portion 7d of the first housing 7 . That is, the second end portion 10 c of the thick portion 10 constitutes part of the second end portion 7 d of the first housing 7 .

A plurality of (for example, 13 in the present embodiment) pin grooves 10 a are formed on an inner peripheral surface 10 d of the thick portion 10 . Each pin groove 10a is formed in the whole thick part 10 along the axial direction, and is arrange|positioned at equal intervals in the circumferential direction. The pin groove 10a is formed in a semicircular shape as viewed from the axial direction. A columnar internal tooth pin (an example of internal teeth in the claims) 90 is rotatably accommodated in each pin groove 10a. Since the pin groove 10 a is formed in a semicircular shape as viewed in the axial direction, the inner tooth pin 90 has a shape protruding radially inward from the inner peripheral surface 10 d of the thick portion 10 by an amount corresponding to a semicircle. The internal tooth pin 90 functions as an internal tooth that meshes with the swing gear 5 discussed later.

On the outer peripheral portion of the thick portion 10, a first through hole 19 penetrating in the axial direction is formed between the respective pin grooves 10a. The plurality of first through holes 19 are arranged at equal intervals in the circumferential direction. The number of first through holes 19 is, for example, thirteen. The rod portions 20a of the bolts (an example of a fixing portion and a screw) 20 are inserted into the plurality of first through holes, respectively. The first casing 7 , the second casing 8 , and the supply and discharge plate 46 discussed later are fastened together by the bolts 20 to be integrated.

Further, on the inner peripheral surface 7 c of the first housing 7 , a first bearing accommodating portion 11 having a larger inner diameter via the stepped portion 11 a is formed at a position closer to the first direction than the thick portion 10 . The outer ring 12 a of the first bearing 12 is fitted into the first bearing housing portion 11 . The positioning between the first bearing 12 and the first housing 7 is performed by the outer ring 12 a abutting against the stepped portion 11 a.

On the inner peripheral surface 7 c of the first housing 7 , a seal accommodating portion 14 having a larger inner diameter via a stepped portion 14 a is formed at a position closer to the first direction than the first bearing accommodating portion 11 . Part of the seal portion 15 is fitted into the seal housing portion 14 . The sealing part 15 seals between the first housing 7 and the rotating part 3 . As the sealing portion 15, for example, a floating seal is used. However, the configuration of the seal portion 15 is not limited to a floating seal. Various sealing materials such as gaskets and mechanical seals can be used for the sealing part 15 .

A first carrier-side first labyrinth portion 16 having an inner diameter larger than that of the seal housing portion 14 is formed at the first end portion 7 b of the first housing 7 . The first labyrinth part 16 on the first carrier side cooperates with the rotating part 3 to form a first labyrinth 38 . Due to the first labyrinth 38 , it is difficult for dust and the like to enter the gap between the first housing 7 and the rotating unit 3 from the outside.

The 2nd end part 7d of the 1st case 7 corresponds to the dividing surface between the 1st case 7 and the 2nd case 8 of the case part 2. As shown in FIG. The entire outer peripheral portion of the second end portion 7d of the first housing 7 is formed flat. An O-ring groove 17 having an annular shape as viewed in the axial direction is formed at a position closer to the outer peripheral portion of the second end portion 7d than the first through hole 19 . An O-ring 18 is attached to the O-ring groove 17 . The O-ring 18 ensures sealing between the first housing 7 and the second housing 8 .

The second housing 8 is formed in an annular shape. In the peripheral wall 8 a of the second housing 8 , a second through hole 22 communicating with the first through hole 19 of the first housing 7 is formed at a position corresponding to the first through hole 19 of the first housing 7 . The second through hole 22 is formed to have the same diameter as that of the first through hole 19 and is located on the same axis as the first through hole 19 . A counterbore portion 23 is formed in most of the second through hole 22 on the second direction side. The head portion 20 b of the bolt 20 is inserted into the counterbore portion 23 .

The first end portion 8 b on the first direction side of the second housing 8 corresponds to a dividing plane with the first housing 7 of the housing portion 2 . A pressure plate 21 protruding radially inward from the inner peripheral surface 8c of the second housing 8 is integrally formed on the first end portion 8b of the second housing 8 . The pressure plate 21 is formed in an annular shape as viewed in the axial direction. The pressure plate 21 closes the working chambers 66a, 66b formed between the inner peripheral surface 7c of the first housing 7 and the outer peripheral surface of the swing gear 5 to be discussed later from the second direction side.

Moreover, when the 1st housing 7 and the 2nd housing 8 are integrated, the pressure plate 21 can be formed separately from the housing part 2. As shown in FIG.

The second carrier-side first labyrinth portion 25 is formed on most of the inner peripheral surface 21 a of the pressure plate 21 except the end portion on the first direction side. The first labyrinth portion 25 on the second carrier side is formed by making the inner diameter larger than the inner diameter of the inner peripheral surface 21 a of the pressure plate 21 via the stepped portion 25 a. The second carrier-side first labyrinth part 25 cooperates with the rotating part 3 to form a second labyrinth 40 . Owing to the second labyrinth 40, it is difficult for hydraulic oil to leak from between the second housing 8 and the rotating part 3 (details will be described later).

On the inner peripheral surface 8 c of the second housing 8 , a second bearing accommodating portion 24 having a larger inner diameter via a stepped portion 24 a is formed at a position closer to the second direction than the pressure plate 21 . The outer ring 13 a of the second bearing 13 is fitted into the second bearing housing portion 24 . The positioning between the second bearing 13 and the second housing 8 is performed by the outer ring 13 a abutting against the stepped portion 24 a.

At the second end portion 8d on the second direction side of the second housing 8, an O-ring groove 26 having an annular shape when viewed in the axial direction is formed on the outer peripheral portion. An O-ring 27 is attached to the O-ring groove 26 . The O-ring 27 ensures sealing between the second housing 8 and a cover 29 to be described later.

On the second end portion 8d of the second housing 8, a plurality of internal thread portions 28 are formed at equal intervals in the circumferential direction at a position radially inward of the O-ring groove 26 . The cover 29 is fixed to the second housing 8 by these internal thread portions 28 .

＜Cover＞

The cover 29 closes the opening 8e of the second case 8 from the second direction side. The cover 29 is formed, for example, by pressing a metal plate so that most of the center bulges toward the second direction side. The outer peripheral portion of the cover 29 has a shape in which an outer flange portion 29a is formed. The outer flange portion 29 a overlaps the second end portion 8 d of the second housing 8 .

A through-hole 29 b penetrating in the thickness direction is formed in the outer flange portion 29 a at a position corresponding to the internal thread portion 28 of the second housing 8 . Bolts 30 are inserted into the through-holes 29 b from the second direction side, and the bolts 30 are fastened to the internally threaded portion 28 of the second housing 8 to fix the cover 29 to the second housing 8 .

＜For row board＞

A supply and discharge plate (port plate) 46 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 arranged at the first end of one side of the thick portion 10 Section 10b. The supply and discharge plate 46 is a plate for supplying hydraulic oil to working chambers 66 a and 66 b to be described later, or for discharging hydraulic oil from the working chambers 66 a and 66 b.

The supply and discharge plate 46 is formed in an annular shape as viewed from the axial direction. The outer diameter of the supply and discharge plate 46 is approximately equal to or slightly smaller than the diameter of the inner peripheral surface 7 c of the first housing 7 . Therefore, the supply and discharge plate 46 is disposed on the first end portion 10 b of the thick portion 10 so as to fit into the inner peripheral surface 7 c of the first housing 7 .

On the outer peripheral portion of the supply and discharge plate 46 , a female thread portion 47 is formed at a position corresponding to the first through hole 19 of the first housing 7 . Bolts 20 are 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 bolts 20 are fastened to the internal thread portion 47 of the supply and discharge plate 46 . Accordingly, the first housing 7 , the second housing 8 , and the supply and discharge plate 46 are jointly fastened by the respective bolts 20 to be integrated.

In the supply and discharge plate 46 , a plurality of through holes (supply and discharge ports) 46 a penetrating in the thickness direction are formed at positions radially inward of the internally threaded portion 47 . Hydraulic oil is supplied to the working chambers 66a and 66b through these through-holes 46a, or hydraulic oil is discharged from the working chambers 66a and 66b (details will be described later). The number of through holes 46 a corresponds to the number of pin grooves 10 a formed in the first housing 7 . For example, in the present embodiment, the number of through-holes 46 a is thirteen. Each through hole 46 a is formed such that the opening on the thick portion 10 side is located at the center between the circumferentially adjacent pin grooves 10 a and radially inward of the inner peripheral surface 10 d of the thick portion 10 .

A plate side labyrinth 48 is formed on most of the inner peripheral surface 46 b of the supply and discharge plate 46 except the end portion on the second direction side. The plate-side labyrinth portion 48 is formed by making the inner diameter larger than the inner diameter of the inner peripheral surface 46 b of the supply and discharge plate 46 via the stepped portion 48 a. The plate-side labyrinth part 48 forms a third labyrinth 49 in cooperation with the rotating part 3 . Owing to the third labyrinth 49, it is difficult for working oil to leak from between the supply and discharge plate 46 and the rotating part 3 (details will be discussed later).

＜Rotating part＞

The rotating part 3 rotatably held by the housing part 2 includes a carrier part (rotating member) 6, a plurality (for example, three in this embodiment) of crankshafts 4, and a swing gear 5 as main constituent elements. . Both axial sides of the carrier portion 6 are rotatably supported via bearings 12 and 13 . The crankshaft 4 is rotatably supported by the carrier portion 6 . The swing gear 5 is rotatably supported by the crankshaft 4 .

The carrier part 6 is divided in the axial direction, and is comprised by the 1st carrier 31 arrange|positioned in the 1st direction side, and the 2nd carrier 32 arrange|positioned in the 2nd direction side.

The first carrier 31 has a disc-shaped base plate 33 integrally formed thereon, and a plurality of (for example, in this embodiment, an 3) The structure of the pillar part 34.

The outer peripheral surface 33c of the substrate portion 33 is gradually formed to have a larger outer diameter through the stepped portion as it goes from the second end portion 33b toward the first end portion 33a on the first direction side.

That is, the outer peripheral surface 33c of the base plate portion 33 has in order from the second end portion 33b side: a first outer peripheral surface 33d; The first direction side end of the surface 33d; the third outer peripheral surface 33f, which is formed on the first direction side end of the second outer peripheral surface 33e in such a manner that the outer diameter is enlarged by the small step portion 33i; and the fourth outer peripheral surface 33g, which The outer diameter is formed on the first direction side end of the third outer peripheral surface 33f so as to be enlarged by the intermediate step portion 33j.

A portion of the first carrier 31 corresponding to the first outer peripheral surface 33 d 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 33 b of the first carrier 31 is located slightly forward of the step portion 48 a of the supply and discharge plate 46 . Thus, the third labyrinth 49 is constituted 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 and discharge plate 46 .

The inner ring 12b of the first bearing 12 is fitted to the third outer peripheral surface 33f. The positioning between the first bearing 12 and the first carrier 31 is performed by the inner ring 12b abutting against the intermediate step portion 33j. Accordingly, the positioning of the first carrier 31 with respect to the first housing 7 is performed. In addition, the first carrier 31 is rotatably supported by the first housing 7 via the first bearing 12 .

The 4th outer peripheral surface 33g of the 1st carrier 31 opposes the seal accommodating part 14 of the 1st housing 7 in a radial direction. That is, the seal portion 15 is disposed between the fourth outer peripheral surface 33 g of the first carrier 31 and the seal housing portion 14 of the first housing 7 .

A disc portion 35 having a circular shape as viewed in the axial direction is integrally formed on the first direction side end of the fourth outer peripheral surface 33g. 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 7 a of the first housing 7 . On the second end portion 35b of the disc portion 35, a seal housing recess 36 having an annular shape when viewed in the axial direction is formed on the outer peripheral portion. The seal housing recess 36 is smoothly connected to the fourth outer peripheral surface 33g. Part of the seal portion 15 is also housed in the seal housing recess 36 . Thereby, the space between the first housing 7 , the first carrier 31 (the rotating portion 3 ) and the seal housing recess 36 is sealed.

On the second end portion 35b of the disc portion 35, a first carrier-side second labyrinth portion 37 having a smaller outer diameter through a step is formed on the outer peripheral edge. The first labyrinth 38 is composed of the first carrier-side second labyrinth portion 37 and the first carrier-side first labyrinth portion 16 formed in the first housing 7 . The first labyrinth 38 is arranged radially outward of the seal portion 15 , and therefore, the intrusion of dust or the like from the outside through the gap between the first case 7 and the first carrier 31 (rotation portion 3 ) can be reliably suppressed.

An outer flange portion 39 protruding radially outward is formed on the outer peripheral surface 35 c of the disc portion 35 . The outer flange portion 39 is used when attaching the hydraulic motor 1 to an unillustrated external device. Through-holes 39 a through which unillustrated bolts are inserted are formed in the outer flange portion 39 so as to penetrate in the thickness direction (axial direction) of the outer flange portion 39 .

At the second end portion 33b of the base plate portion 33, a plurality of (for example, in this embodiment, There are 3 in the center) the bearing recess 44. The shaft support recess 44 rotatably supports the crankshaft 4 . A first bearing 59 a for rotatably supporting the crankshaft 4 is fitted in the shaft support recess 44 . The first bearing 59a is, for example, a sliding bearing. However, the structure of the first bearing 59a is not limited to a sliding bearing. Various bearings, such as a ball bearing, can be used for the 1st bearing 59a.

In addition, in the base plate portion 33, a plurality of supply paths 41, a plurality of discharge paths 42, and a liquid discharge path (tank) are integrally formed in the axial direction of the base plate portion 33 at a position radially inward of the second outer peripheral surface 33e. path)43.

The supply path 41 is an oil passage for supplying hydraulic oil from a hydraulic pump not shown. The second direction side end of the supply path 41 is opened via the large step portion 33h. That is, each supply path 41 has the supply opening part 41a in the large step part 33h.

The discharge passage 42 is an oil passage for discharging hydraulic oil in the hydraulic motor 1 . The second direction side end of the discharge path 42 is also opened via the large step portion 33h. That is, each discharge path 42 has the discharge opening part 42a in the large step part 33h.

The number of supply paths 41 and the number of discharge paths 42 are different from the number of through holes 46 a of the supply and discharge plate 46 fixed to the first housing 7 . For example, in this embodiment, the number of supply paths 41 and the number of discharge paths 42 are 12 less than the number of through holes 46 a of the supply and discharge plate 46 , respectively.

The supply openings 41 a of the supply path 41 and the discharge openings 42 a of the discharge path 42 are alternately arranged on the same pitch circle in the circumferential direction. A plurality of supply openings 41 a and a plurality of discharge openings 42 a are arranged at equal intervals in the circumferential direction so that one supply opening 41 a and one discharge opening 42 a form a pair.

The drain passage 43 is a flow path for returning hydraulic fluid leaked from the hydraulic motor 1 to a tank not shown.

The first direction side ends of the supply path 41 , the discharge path 42 , and the drain path 43 communicate with the oil distribution portion 45 provided at the first end portion 33 a on the first direction side of the substrate portion 33 . The oil distribution unit 45 has a plurality of distribution channels not shown. Hydraulic oil from the hydraulic pump is supplied to the supply path 41 through these distribution flow paths. In addition, the hydraulic oil discharged to the discharge path 42 flows back to the tank through the distribution flow path or flows back to the supply path 41 again. The hydraulic oil discharged into the drain passage 43 also flows back to the tank through the distribution flow passage. In addition, details about the action of the working oil will be discussed later.

A gap is formed between the large step portion 33h of the first carrier 31 and the supply and discharge plate (port plate) 46 . A slide plate (piston plate) 50 is disposed in the gap. The slide plate 50 is formed in an annular shape as viewed in the axial direction. The slide plate 50 is provided so that the inner peripheral surface is fitted to the first outer peripheral surface 33d of the first carrier 31 , is non-rotatable with respect to the first carrier 31 , and is slidably movable in the axial direction. The thickness of the slide plate 50 is smaller than the gap between the large step portion 33 h and the supply and discharge plate 46 .

A plurality of through holes (through ports) 50 c are formed in the slide plate 50 so as to correspond to the supply opening 41 a of the supply path 41 and the discharge opening 42 a of the discharge path 42 . The through-hole 50c corresponding to the supply opening 41a is arranged on the same axis as the supply opening 41a. The through hole 50c corresponding to the discharge opening 42a is arranged on the same axis as the discharge opening 42a.

A cylindrical piston 51 is provided in each supply opening 41a and each discharge opening 42a. The piston 51 is slidably provided on the supply path 41 and the discharge path 42 . The piston 51 is urged toward the slide plate 50 by springs (not shown) provided in the supply path 41 and the discharge path 42 . Accordingly, the piston 51 is pressed against the slide plate 50 .

The thickness of the slide plate 50 is smaller than the gap between the large step portion 33 h and the supply and discharge plate 46 . Therefore, the piston 51 protrudes from the large step portion 33h by the spring and comes into contact with the slide plate 50 . As a result, the slide plate 50 is pressed against the supply and discharge plate 46 . Accordingly, each supply path 41 communicates with the through-hole 50 c of the slide plate 50 via the piston 51 . In addition, each discharge path 42 communicates with the through-hole 50 c of the slide plate 50 via the piston 51 . Furthermore, each through hole 50 c of the slide plate 50 communicates with the through hole 46 a of the supply and discharge plate 46 .

The pillar portion 34 of the first carrier 31 has a triangular column shape when viewed in the axial direction. Each pillar portion 34 is disposed so as to be located between the shaft support recessed portions 44 of the base plate portion 33 in the circumferential direction. That is, each pillar part 34 is arrange|positioned at the 2nd end part 33b of the board|substrate part 33 at equal intervals in the circumferential direction. The pitch circle diameter (Japanese: ピッチテル diameter) of each pillar portion 34 is substantially the same as the pitch circle diameter of the shaft support recessed portion 44 .

The tip end portion 34a of the pillar portion 34 is formed flat. The tip end portion 34a of the pillar portion 34 is located on the same plane as the second end portion 7d of the first housing 7 . A female thread portion 52 for a close-fitting bolt is formed at the tip end portion 34 a of the pillar portion 34 .

The female thread portion 52 for tight fitting bolts includes: a fitting concave portion 52a formed in the axial direction from the top end portion 34a of the pillar portion 34 to the axial center of the pillar portion 34; and an internal thread portion main body 52b formed from the The bottom of the fitting recess 52a extends in the first direction. The first carrier 31 and the second carrier 32 are integrated by fastening the fit bolt (an example of another fixing portion) 53 to the female thread portion 52 for the fit bolt.

The second carrier 32 is formed in a disc shape. The second carrier 32 is positioned so that the first end portion 32 a on the first direction side comes into contact with the tip end portion 34 a of the pillar portion 34 constituting the first carrier 31 . Therefore, a gap equal to the height of the pillar portion 34 is formed between the base plate portion 33 of the first carrier 31 and the second carrier 32 . The thick portion 10 of the first housing 7 surrounds the gap to form a swing gear housing portion 60 for housing the swing gear 5 .

The first end portion 32a of the second carrier 32 is formed flat as a whole. In the second carrier 32 , a fitting hole 54 penetrating in the thickness direction is formed at a position corresponding to the female thread portion 52 for a fastening bolt. Insert the tight fit bolt 53 into the fitting hole 54 from the second direction side of the second carrier 32, and fasten the tight fit bolt 53 to the female thread part main body 52b through the fitting recess 52a of the pillar part 34, thereby making the second The first carrier 31 and the second carrier 32 are integrated.

The tight fit bolt 53 includes: a stem portion 53a; an external thread portion 53b protruding from the first direction side end of the stem portion 53a and formed on the same axis as the stem portion 53a; and a head portion 53c formed on the first direction side end of the stem portion 53a. The two-direction side end is formed on the same axis as the rod portion 53a. In the state where the tight fitting bolt 53 is fastened to the inner threaded portion 52 for the tight fitting bolt, the rod portion 53 a of the tight fitting bolt 53 fits into the fitting recess 52 a of the pillar portion 34 and the fitting hole 54 of the second carrier 32 . combine. That is, the rod portion 53 a of the fastening bolt 53 is arranged to straddle the first carrier 31 and the second carrier 32 .

A counterbore portion 55 is formed in the fitting hole 54 at the second end portion 32 b on the second direction side of the second carrier 32 . The head portion 53 c of the fit bolt 53 is inserted into the counterbore portion 55 . Thereby, the protrusion height of the head part 53c of the fastening bolt 53 from the 2nd end part 32b of the 2nd carrier 32 is suppressed.

Most of the outer peripheral surface 32c of the second carrier 32 in the center in the axial direction has a reduced-diameter portion 56 whose outer diameter is formed to be small by a stepped portion 56a. The inner ring 13 b of the second bearing 13 is fitted into the reduced diameter portion 56 . As a result, the second carrier 32 is rotatably supported by the second housing 8 via the second bearing 13 .

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

The front end of the second labyrinth portion 57 on the second carrier side is positioned slightly forward of the step portion 25 a of the first labyrinth portion 25 on the second carrier side. Thus, the second labyrinth 40 is constituted 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 .

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

＜Crankshaft＞

Each crankshaft 4 is rotatably supported by each shaft support recessed part 44 and shaft support hole 58 via each bearing 59a, 59b. It can be said that the crankshaft 4 can slide and rotate in the shaft support recessed part 44 and the shaft support hole 58 via the bearings 59a and 59b.

In this embodiment, the number of crankshafts 4 is three. The crankshaft 4 has integrally formed bearing portions 4a, 4b (first bearing portion 4a, second bearing portion 4b) rotatably supported on the shaft support recessed portion 44 and the shaft support hole 58 via bearings 59a, 59b, and is provided on each The structure of the cylindrical eccentric part 4c between the bearing part 4a, 4b.

The rotation axis (second axis) C2 of the crankshaft 4, that is, the axes of the bearings 4a and 4b are parallel to the first axis C1. The movement of the crankshaft 4 in the axial direction is supported by the thrust bearings 61a, 61b (first thrust bearing 61a, second thrust bearing 61b) provided on the axially outer sides of the respective bearing portions 4a, 4b and the shaft on the first carrier 31. The first collar 70 a provided in the recess 44 is restricted by the second collar 70 b provided in the shaft support hole 58 of the second carrier 32 . Of the two thrust bearings 61 a and 61 b , the movement of the second thrust bearing 61 b provided in the shaft support hole 58 of the second carrier 32 in the second direction is restricted by the stop ring 62 provided in the shaft support hole 58 .

The axial length of the eccentric portion 4 c is formed to be within the axial width of the swing gear housing portion 60 . Specifically, the length of the eccentric portion 4 c in the axial direction is slightly shorter than the length of the thick portion 10 of the first housing 7 in the axial direction. Therefore, the position of the end portion of the eccentric portion 4c on the second direction side and the position of the first end portion 8b of the second housing 8 are substantially on the same plane.

The axis line (third axis line) C3 of the eccentric portion 4 c is eccentric with respect to the second axis line C2 of the crankshaft 4 . The swing gear 5 is rotatably supported on the eccentric portion 4c via a third bearing 59c. The third bearing 59c is, for example, a sliding bearing. However, the structure of the third bearing 59c is not limited to a sliding bearing. Various bearings such as ball bearings can be used for the third bearing 59c.

The outer diameter of the swing gear 5 is smaller than the diameter of the inner peripheral surface 10 d of the thick portion 10 so that it can be accommodated in the swing gear storage portion 60 . The axial thickness of the swing gear 5 is equal to the axial thickness of the eccentric portion 4c. Therefore, the position of the end portion of the swing gear 5 on the second direction side and the position of the first end portion 8 b of the second housing 8 are substantially on the same plane. In the swing gear 5 , a support hole 63 through which the eccentric portion 4 c of the crankshaft 4 penetrates is formed at a position corresponding to the crankshaft 4 .

The support holes 63 are arranged at equal intervals in the circumferential direction. The third bearing 59c is provided in these support holes 63 . The movement of the swing gear 5 in the axial direction relative to the crankshaft 4 is restricted by stop rings 67 provided at both axial ends of the third bearing 59c. Based on such a structure, the rotation of the swing gear 5 is restricted to swing rotation by the crankshaft 4 .

Also, in the swing gear 5 , an escape hole 64 through which the pillar portion 34 is inserted is formed at a position corresponding to the pillar portion 34 of the first carrier 31 . The shape of the avoidance hole 64 as viewed in the axial direction is a triangular shape corresponding to the shape of the pillar portion 34 as viewed in the axial direction. The escape hole 64 is formed sufficiently larger than the outer surface shape of the pillar portions 34 so that each pillar portion 34 does not interfere with the swinging rotation of the swing gear 5 .

The outer peripheral surface of the swing gear 5 faces the inner tooth pin 90 of the first housing 7 in the radial direction. External teeth 65 that mesh with internal tooth pins 90 are formed on the outer peripheral surface of the swing gear 5 . The number of teeth of the external teeth 65 is different from the number (number) of teeth of the internal tooth pins 90 . For example, in the present embodiment, the number of teeth of the external teeth 65 is 12, which is one less than the number of teeth of the inner tooth pins 90 . This number corresponds to the number of supply paths 41 and the number of discharge paths 42 formed on the first carrier 31 .

During the oscillating rotation operation, any part of the oscillating gear 5 from the tooth top 65 a to the tooth bottom 65 b is always in contact with the inner tooth pin 90 . Thus, two working chambers 66a, 66b (the first working chamber 66a, the second working chamber 66a) are substantially formed between the inner peripheral surface 10d of the thick portion 10 of the first housing 7 and the outer teeth 65 of the swing gear 5. Studio 66b). The two working chambers 66a, 66b are formed line-symmetrically as seen from the axial direction.

The plurality of through-holes 46a of the supply and discharge plate (port plate) 46 communicate with these working chambers 66a, 66b. Hydraulic oil is supplied to the working chambers 66a and 66b through these through-holes 46a, and hydraulic oil is discharged from the working chambers 66a and 66b. Thus, the hydraulic motor 1 is rotationally driven.

＜Brake Mechanism＞

FIG. 5 is an enlarged view of a V portion in FIG. 1 , showing a released state of the brake mechanism 100 . FIG. 6 is an enlarged view of the V portion in FIG. 1 , showing an engaged state of the brake mechanism 100 .

The hydraulic motor 1 includes a brake mechanism 100 as its parking brake. The parking brake refers to a brake that is released when the hydraulic motor 1 is driven, and is applied while being applied.

The brake mechanism 100 includes a stopper engaging portion 101, a stopper 102, a piston 103, a cylinder 104, a spring 105, and a branch flow path 41g.

The stopper engaging portion 101 is formed penetratingly at the center of the swing gear 5 . The stopper engaging portion 101 has an axis C5 parallel to the first axis C1. In addition, the stopper engaging portion 101 moves around the first axis C1 as the swing gear 5 swings, and is shown as an axis C5 in FIG. 5 .

The cylinder 104 opened at the second end portion 33 b is formed on the substrate portion 33 facing the first direction side of the stopper engaging portion 101 . A piston 103 is accommodated inside the cylinder 104 . The cylinder 104 has an axis C5 parallel to the first axis C1. The piston 103 can reciprocate inside the cylinder 104 along an axis C5 that is a direction along the axis C1.

Inside the cylinder 104 , a spring (pressing portion) 105 is disposed on the first direction side of the piston 103 . The spring 105 presses the piston 103 in the second direction. Inside the cylinder 104 , a branch channel 41 g is connected to a position on the second direction side of the piston 103 . The branch flow path 41g is connected to the pressure chamber 104a of the cylinder 104 on the second direction side of the piston 103 . The branch flow path 41g branches from the supply path 41 .

The branch flow path 41g can supply the hydraulic oil (working fluid) branched from the supply path 41 to the pressure chamber 104a. In the pressure chamber 104a supplied with hydraulic oil, the piston 103 is pressed toward the first direction. When the pressure applied to the piston 103 from the hydraulic oil in the pressure chamber 104a is greater than the pressing force of the spring 105, the piston 103 moves in the first direction.

When the pressure applied to the piston 103 from the operating oil in the pressure chamber 104a is smaller than the urging force of the spring 105 and when the operating oil is not supplied to the pressure chamber 104a, due to the urging force of the spring 105, the piston 103 can move toward the second 2 directions to move.

The end portion of the piston 103 in the second direction forms the stopper 102 so as to have the same diameter as the stopper engaging portion 101 . The stopper 102 and the stopper engaging portion 101 have the same cross-sectional shape. The cross-sectional shape of the stopper 102 and the stopper engaging portion 101 can be circular or polygonal.

The stopper 102 moves along the axis C5 in a contactable and separable manner with respect to the swing gear 5 as the piston 103 reciprocates. The stopper 102 can protrude in the second direction from the second end portion 33 b of the substrate portion 33 by the biasing force of the spring 105 . When the stopper 102 has moved in the second direction, the stopper 102 is inserted into the stopper engaging portion 101 . At this time, depending on the swing rotation position of the swing gear 5, the position of the stopper 102 and the stopper engaging portion 101 may not be aligned, but the stopper 102 and the stopper engagement portion 101 are not aligned during one rotation of the output of the gear frame portion 6. The positions of the component 102 and the engaging portion 101 of the stopper must be aligned. If the positions of the stopper 102 and the stopper engagement portion 101 are aligned, the stopper 102 is inserted into the stopper engagement portion 101 .

When the stopper 102 is inserted into the stopper engaging portion 101 , the stopper 102 stops the swinging rotation of the swing gear 5 .

The stopper 102 is inserted into the stopper engaging portion 101 by the urging force of the spring 105 before the hydraulic oil is supplied to the pressure chamber 104 a. When hydraulic oil is supplied to the pressure chamber 104a through the branch flow path 41g, the force generated by the stopper 102 becomes larger than the pressing force of the spring 105 due to the action of the hydraulic oil. As a result, the stopper 102 presses the piston 103 in the first direction. When the piston 103 moves in the first direction, the stopper 102 moves in the first direction and is pulled out from the stopper engaging portion 101 . Furthermore, the stopper 102 separated from the swing gear 5 is located closer to the first direction than the second end portion 33 b of the base plate portion 33 , and is housed inside the cylinder 104 .

The spring 105 , the piston 103 and the cylinder 104 as the pressing release portion, and the branch flow path 41 g constitute the stopper moving portion 100 a.

＜Motion of hydraulic motor＞

Hereinafter, the operation of the hydraulic motor 1 will be described in detail.

In the hydraulic motor 1 , hydraulic oil supplied from a hydraulic pump (not shown) is supplied to each supply path 41 via an oil distribution portion 45 . The hydraulic oil supplied to each supply path 41 is supplied to the working chambers 66 a , 66 b through the piston 51 of each supply opening 41 a , the through hole 50 c of the slide plate 50 , and the through hole 46 a of the supply and discharge plate (port plate) 46 .

Among them, the piston 51 of each supply opening 41 a slides relative to the slide plate 50 that rotates integrally with the first carrier 31 in a state of being pressed toward the slide plate 50 by a spring. When the through hole 50 c is brought to a position aligned with the piston 51 by the rotation of the slide plate 50 , the hydraulic oil supplied to the supply path 41 flows into the through hole 50 c.

The slide plate 50 that rotates integrally with the first carrier 31 slides with respect to the supply and discharge plate (port plate) 46 integrally provided with the case portion 2 . When the through hole 46a is aligned with the through hole 50c due to the rotation of the slide plate 50 and the supply/discharge plate 46, the hydraulic oil supplied to the through hole 50c flows into the through hole 46a.

In addition, when the through hole 46 a is not aligned with the through hole 50 c and does not communicate, the through hole 46 a is blocked by the slide plate 50 . Thereby, hydraulic oil is prevented from leaking or flowing back from the working chambers 66a, 66b via the through-hole 46a.

Among them, the number of supply paths 41 (supply opening 41 a and through hole 50 c communicating with supply opening 41 a of slide plate 50 ) is one less than the number of through hole 46 a of supply and discharge plate 46 . Also, the number of discharge paths 42 (discharge opening 42 a and through-hole 50 c communicating with discharge opening 42 a of slide plate 50 ) is one less than the number of through-holes 46 a of supply and discharge plate 46 . Therefore, only the supply path 41 communicates with either one of the two working chambers 66 a and 66 b through the through hole 46 a of the supply and discharge plate 46 . In addition, only the discharge path 42 communicates with the other one of the two working chambers 66 a and 66 b through the through hole 46 a of the supply and discharge plate 46 .

Then, the internal pressure of any one of the two working chambers 66a, 66b is higher than the internal pressure of any other of the two working chambers 66a, 66b. Hereinafter, in order to make the description easy to understand, among the two working chambers 66a, 66b, the pressure of the working chamber 66a (the left side in FIG. 2 ) is higher than the pressure of the working chamber 66b (the right side in FIG. 2 ). Be explained. In addition, in the following description, the working chamber 66a having a relatively high pressure is referred to as a high-pressure working chamber 66a. The working chamber 66b having a lower pressure than the high-pressure working chamber 66a is called a low-pressure working chamber 66b. The high-pressure working chamber 66 a communicates with the supply path 41 . The low-pressure working chamber 66 b communicates with the discharge path 42 .

By supplying hydraulic oil to the high-pressure working chamber 66a, the swing gear 5 is pushed toward the low-pressure working chamber 66b side (see arrow Y1 in FIG. 2 ). The working oil in the low-pressure working chamber 66 b is discharged through the discharge path 42 . As a result, the internal tooth pin 90 meshes with the external tooth 65 of the swing gear 5 on the side of the low-pressure working chamber 66b. Then, since the number of teeth of the external teeth 65 is one less than the number of teeth of the internal tooth pins 90 , the swing gear 5 is slightly deviated in the rotational direction.

At this time, the carrier portion 6 is deviated in the rotational direction along with the swing gear 5 by the crankshaft 4 . That is, the rotating part 3 is slightly rotated with respect to the case part 2 . Then, the slide plate 50 rotates relative to the supply and discharge plate 46 . Then, the state in which the through-hole 50c of the slide plate 50 communicates with the through-hole 46a of the supply and discharge plate 46 is switched. Since the swing gear 5 swings and rotates, the high-pressure working chamber 66a also deviates slightly in the direction of rotation relative to the low-pressure working chamber 66b.

When the communication state between the through-hole 50c of the slide plate 50 and the through-hole 46a of the supply/discharge plate 46 is switched, hydraulic oil is supplied to the high-pressure working chamber 66a again. In addition, hydraulic oil is discharged from the low-pressure working chamber 66b. By repeating this operation sequentially, the rotating part 3 rotates relative to the housing part 2 . Use this rotation to get output.

When the through hole 46a is aligned with the through hole 50c due to the rotation of the slide plate 50 and the supply and discharge plate 46, the working oil is discharged from the low pressure working chamber 66b to the through hole 50c.

In addition, when the through hole 46a is not aligned with the through hole 50c and does not communicate, the through hole 46a is blocked by the slide plate 50 to prevent hydraulic oil from being discharged from the working chambers 66a, 66b through the through hole 46a.

The piston 51 of the discharge opening 42 a of the discharge path 42 slides relative to the slide plate 50 that rotates integrally with the first carrier 31 while being pressed toward the slide plate 50 by a spring. When the through hole 50 c is aligned with the piston 51 by the rotation of the slide plate 50 , the hydraulic oil discharged from the through hole 46 a is discharged to the discharge passage 42 through the piston 51 of the discharge opening 42 a. The hydraulic oil discharged to the discharge path 42 returns to the tank through the distribution flow path.

In this way, the hydraulic motor 1 utilizes the discrepancy between the number of the supply path 41 (the supply opening 41 a and the through hole 50 c communicating with the supply opening 41 a of the slide plate 50 ) and the number of the through hole 46 a of the supply and discharge plate 46 and the discharge path. 42 (the discharge opening 42a and the through-hole 50c communicating with the discharge opening 42a of the slide plate 50) is inconsistent with the number of the through-hole 46a of the supply and discharge plate 46, thereby sequentially switching the slide plate 50 in the circumferential direction. The state where the through hole 50c communicates with the through hole 46a of the supply and discharge plate 46 . As a result, hydraulic oil is selectively supplied and discharged from the through holes 46a of the supply and discharge plate 46 to and from the working chambers 66a and 66b, and the rotary unit 3 rotates.

The carrier part 6 constituting the rotating part 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 by the fit bolts 53 , power transmission between the first carrier 31 and the second carrier 32 is performed via the fit bolts 53 . The rod portion 53 a of the tight fit bolt 53 is arranged to straddle the first carrier 31 and the second carrier 32 . Therefore, power transmission between the first carrier 31 and the second carrier 32 is efficiently performed compared to the case where the external thread portion 53b straddles between the first carrier 31 and the second carrier 32 .

Wherein, on the first direction side of the swing gear 5 , the third labyrinth 49 is composed of the first outer peripheral surface 33 d of the first gear carrier 31 , the second end portion 33 b , and the plate-side labyrinth portion 48 of the supply and discharge plate 46 . On the second direction side of the swing gear 5 , the second labyrinth 40 is composed of 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 . Therefore, it is difficult for the working oil leaked from the working chambers 66a, 66b to pass through the small gap between the crankshaft 4 and the swing gear 5 from between the first housing 7 and the first gear carrier 31 and between the second housing 8 and the second gear carrier 32. leakage.

In addition, in the hydraulic motor 1 , by fixing the housing portion 2 , an output can be obtained from the rotating portion 3 . In this case, the external device fixed to the outer flange part 39 of the rotating part 3 (1st carrier 31) becomes a to-be-rotated body. In addition, by fixing the rotating part 3, an output can also be obtained from the case part 2. FIG. In this case, the external device fixed to the outer flange portion 9 of the casing portion 2 (first casing 7 ) becomes a to-be-rotated body.

The hydraulic motor 1 has an inner tooth pin 90 provided on the first housing 7 . The rotating part 3 includes: a carrier part 6 ; a crankshaft 4 rotatably supported by the carrier part 6 ; With such a configuration, the hydraulic motor 1 can be rotationally driven by supplying or discharging hydraulic oil to and from the working chambers 66a, 66b formed between the inner peripheral surface 7c of the first housing 7 and the outer peripheral surface of the swing gear 5 . Higher torques can be obtained with this rotary drive. The case part 2 which is divided and constructed can be preferably used for such a hydraulic motor 1 .

The hydraulic motor 1 has a supply and discharge plate 46 for selectively supplying and discharging working oil to and from the working chambers 66a and 66b. The supply and discharge plate 46 is disposed on the first end portion 10b of the thick portion 10 (the end on the first direction side of the swing gear 5 ). Such a supply and discharge plate 46 is fixed to the first housing 7 with bolts 20 . The supply and discharge plate 46 is also fixed by the bolts 20 for fixing the first housing 7 and the second housing 8 .

In the hydraulic motor 1, when hydraulic oil is selectively supplied to the working chambers 66a and 66b, the hydraulic oil is branched from the branch flow path 41g and supplied to the pressure chamber 104a.

In a state where hydraulic oil is not supplied from the hydraulic pump, hydraulic oil is not supplied to the pressure chamber 104a. Therefore, in the brake mechanism 100 , the piston is pressed in the second direction by the urging force of the spring 105 . In this state, as shown in FIG. 6 , the stopper 102 is inserted into the stopper engagement portion 101 so that the swing gear 5 does not swing. Therefore, the hydraulic motor 1 is not driven. That is, the state where the brake is applied is maintained. In this state, the brake mechanism 100 functions as a parking brake.

In this state, when hydraulic oil is supplied to the pressure chamber 104a, the pressure of the hydraulic oil in the pressure chamber 104a becomes higher than the pressing force of the spring 105, and the piston 103 moves in the first direction. Then, as shown in FIG. 5 , the stopper 102 is pulled out from the stopper engaging portion 101 to release the restriction on the swing gear 5 . Thereby, the swing gear 5 can swing, and the hydraulic motor 1 is driven.

In addition, the supply of hydraulic fluid to the pressure chamber 104a may be supplied from the hydraulic pump for driving the hydraulic motor 1 that supplies hydraulic fluid to the working chambers 66a, 66b, or may be other pilot pressures.

Thus, in the above-mentioned embodiment, the brake mechanism 100 can be operated as a parking brake by the stopper moving part 100a using the hydraulic fluid used for driving the spring 105 and the hydraulic motor 1. Thus, in the so-called cycloidal hydraulic motor 1 using the swing gear, the crankshaft 4 and the stopper 102 can be constituted as independent components. Therefore, it is possible to prevent the crankshaft 4 and the stopper 102 from performing unified operations such as integrally rotating. Therefore, the resistance to the driving of the hydraulic motor 1 can be reduced to reduce energy consumption. Furthermore, as an effect, it is possible to advance and retreat only the stopper 102 reciprocated by the cylinder 104 provided on the base plate 33 , the piston 103 and the spring 105 relative to the stopper engaging part 101 provided on the swing gear 5 . Simple construction, and cheaply provided.

Furthermore, it can be made compact by a simple structure in which the stopper 102 driven by the cylinder 104 provided on the base plate 33 , the piston 103 , and the spring 105 advances and retreats relative to the stopper engaging part 101 provided on the swing gear 5 . realized. Since it is possible to realize a simple structure that advances and retreats with respect to the stopper engaging portion 101 provided on the swing gear 5 , processing is easy. Since the cylinder 104 and the piston 103 are provided on the base plate portion 33, it is easy to form the branch flow path 104g for supplying hydraulic oil for releasing the brake. In addition, since the substrate portion 33 is a non-rotating portion, it is possible to easily form a flow path. Furthermore, since only one branch flow path 41g is formed, the hydraulic oil for brake driving can be supplied to the cylinder 104, so that space saving can be achieved.

In addition, the arrangement of the crankshaft 4, the cylinder 104, and the piston 103 can be easily performed. Moreover, the brake can be performed only by the action of inserting the stopper 102 into the stopper engaging portion 101, so that the stopper 102 and the inclination between the stopper engaging portion 101 can be avoided. Take action. As a result, reliable braking operation can be realized with a reduced number of parts.

Hereinafter, a rotating machine according to a second embodiment of the present invention will be described based on the drawings.

FIG. 7 corresponds to the enlarged view of the V portion in FIG. 1 , and shows a released state of the brake mechanism 100 in this embodiment. FIG. 8 corresponds to the enlarged view of the V portion in FIG. 1 , and shows an engaged state of the brake mechanism 100 . This embodiment is different from the above-mentioned first embodiment in terms of the stopper moving unit. Components corresponding to the above-mentioned first embodiment other than the stopper moving portion are given the same reference numerals, and descriptions thereof are omitted.

As shown in FIG. 7 , the stopper moving part 100 a of the present embodiment has a cylinder 106 formed on the second carrier 32 . The cylinder 106 is opened to face the swing gear 5 on the first direction side. The second direction side of the cylinder 106 has a communication port facing the cover 29 . Inside the cylinder 106, the stopper 102 is housed on the first direction side. Cylinder 106 may also have the same diameter as 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 reciprocable inside the cylinder 106 along an axis C5 which is a direction along the axis C1.

Inside the cylinder 106 , a spring 105 is disposed on the second direction side of the stopper 102 . The spring 105 presses the stopper 102 in the first direction.

A connecting member 102a along the axis C5 is connected to the stopper 102 on the first direction side. The connection member 102 a is connected coaxially with the axis C5 of the stopper 102 . The piston 103 is connected to the end portion on the first direction side of the coupling member 102a. The stopper 102, the coupling member 102a, and the piston 103 are integrally movable in a direction along the axis C5. The connecting member 102a is disposed inside the stopper engaging portion 101 . The coupling member 102 a has a diameter smaller than that of the stopper engaging portion 101 . Even if the swing gear 5 swings and rotates, the coupling member 102 a does not come into contact with the stopper engaging portion 101 .

Piston 103 is housed in cylinder 104 . The cylinder 104 is arranged coaxially with the cylinder 106 on both sides in the thickness direction of the swing gear 5 . The cylinder 104 on the first direction side of the swing gear 5 and the cylinder 106 on the second direction side of the swing gear 5 are formed as continuous cylinders in the axis C5 direction. That is, the cylinder 104 and the cylinder 106 are formed on the carrier portion 6 .

Inside the cylinder 104 , a branch flow path 41 g is connected to a position on the first direction side of the piston 103 . The branch flow path 41g is connected to the pressure chamber 104b of the cylinder 104 on the first direction side of the piston 103 . The branch flow path 41g branches from the supply path 41 .

The branch flow path 41g can supply hydraulic oil branched from the supply path 41 to the pressure chamber 104b. The piston 103 is pressed in the second direction in the pressure chamber 104b supplied with hydraulic oil. When the pressure applied to the piston 103 from the operating oil in the pressure chamber 104b is greater than the pressing force of the spring 105 of the cylinder 106 pressing the stopper 102 in the first direction, the piston 103 and the stopper 102 move in the second direction.

The stopper 102 is movable in a contactable and separable manner relative to the swing gear 5 along the axis C5 integrally with the coupling member 102 a and the piston 103 . The stopper 102 can protrude in the first direction from the first direction end portion 32 d of the second carrier 32 by the biasing force of the spring 105 . When the stopper 102 has moved in the first direction, the stopper 102 is inserted into the stopper engaging portion 101 . At this time, depending on the swing rotation position of the swing gear 5, the position of the stopper 102 and the stopper engaging portion 101 may not be aligned, but the stopper 102 and the stopper engagement portion 101 are not aligned during one rotation of the output of the gear frame portion 6. The positions of the component 102 and the engaging portion 101 of the stopper must be aligned. If the positions of the stopper 102 and the stopper engagement portion 101 are aligned, the stopper 102 is inserted into the stopper engagement portion 101 .

When the stopper 102 is inserted into the stopper engaging portion 101 , the stopper 102 stops the swinging rotation of the swing gear 5 .

The stopper 102 is inserted into the stopper engaging portion 101 by the urging force of the spring 105 before supplying hydraulic oil to the pressure chamber 104b. When hydraulic oil is supplied to the pressure chamber 104b through the branch flow path 41g, the force of the stopper 102 becomes larger than the pressing force of the spring 105 by the action of the hydraulic oil. Accordingly, the stopper 102 presses the piston 103 in the second direction. When the piston 103 moves in the second direction, the stopper 102 integrated via the connection member 102 a moves in the second direction and is pulled out from the stopper engaging portion 101 . Furthermore, the stopper 102 separated from the swing gear 5 is located closer to the second direction than the first direction end 32 d of the second carrier 32 , and is housed inside the cylinder 106 .

In the present embodiment as well, in the hydraulic motor 1 , hydraulic oil is supplied to the working chambers 66 a , 66 b via the supply path 41 from a hydraulic pump (not shown). As a result, the swing gear 5 is slightly deviated in the rotational direction by the hydraulic oil supplied to the working chambers 66a and 66b to obtain a rotational output. At the same time, hydraulic oil is supplied from the supply path 41 to the pressure chamber 104b via the branch flow path 41g.

In a state where hydraulic oil is not supplied from the hydraulic pump, hydraulic oil is not supplied to the pressure chamber 104b. Therefore, in the brake mechanism 100 , the piston is pressed in the first direction by the urging force of the spring 105 . In this state, as shown in FIG. 8 , the stopper 102 is inserted into the stopper engagement portion 101 so that the swing gear 5 does not swing. Therefore, the hydraulic motor 1 is not driven. That is, the state where the brake is applied is maintained. In this state, the brake mechanism 100 functions as a parking brake.

In this state, when hydraulic oil is supplied to the pressure chamber 104b, the pressure of the hydraulic oil in the pressure chamber 104b becomes higher than the pressing force of the spring 105, and the piston 103 moves in the second direction as shown in FIG. 7 . Then, the stopper 102 moved by the coupling member 102a is pulled out from the stopper engaging portion 101, and the restriction on the swing gear 5 is released. Thereby, the swing gear 5 can swing, and the hydraulic motor 1 is driven.

In addition, the supply of hydraulic fluid to the pressure chamber 104b may be supplied from the hydraulic pump for driving the hydraulic motor 1 that supplies hydraulic fluid to the working chambers 66a, 66b, or may be other pilot pressures.

Also in this embodiment, the brake mechanism 100 can be operated as a parking brake by the stopper moving part 100 a using the spring 105 and the hydraulic oil used for driving the hydraulic motor 1 . Thereby, effects equivalent to those of the above-described embodiment can be achieved.

Furthermore, since the cylinder 106 is formed in the second carrier 32 , there is no need to form a space for accommodating 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 direction side with respect to the piston 103 . Therefore, space saving of the board|substrate part 33 can be aimed at.

In each of the above-mentioned embodiments, the rotation of the swing gear 5 is stopped by the stopper 102 , but as the brake mechanism 100 , the object whose rotation is stopped by the stopper can be the crankshaft 4 . In this case, the crankshaft 4 is preferably located in the center of the pendulum gear 5 .

In addition, in each of the above-mentioned embodiments, the stopper engaging portion 101 is formed so as to penetrate through the swing gear 5 , but it may also be formed as a recess for engaging the stopper 102 without passing through.

Alternatively, the stopper 102 may be configured such that the stopper 102 comes into contact with the swing gear 5 or the crankshaft 4 and presses them to stop the rotation.

In the embodiments disclosed in this specification, a member composed of a plurality of objects may be integrated, and conversely, a member composed of a single object may be divided into a plurality of objects. It does not matter whether it is integrated or not, as long as the object of the invention can be achieved.

Claims (9)

1. A rotary apparatus, wherein,

the rotating device is provided with:

a housing portion having an axis;

an internal tooth provided on an inner peripheral surface of the housing portion;

a carrier portion rotatably supported by the housing portion about the axis;

a crankshaft rotatably supported by the carrier portion about another axis parallel to the axis;

a swing gear which is restricted to swing rotation by the crankshaft and meshes with the internal teeth;

a plurality of supply/discharge channels for supplying a working fluid between the inner peripheral surface of the housing section and the swing gear and discharging the working fluid from between the inner peripheral surface of the housing section and the swing gear;

a stopper that is contactably and detachably movable with respect to any one of the swing gear and the crankshaft; and

and a stopper moving portion that presses or releases the stopper toward the swing gear so that the stopper can be moved toward the swing gear or the crankshaft in a contact-capable and separation-capable manner.

2. The rotating apparatus according to claim 1, wherein,

the stopper presses the swing gear to stop the swing rotation.

3. The rotating apparatus according to claim 1 or 2, wherein,

the stopper moving portion moves the stopper in a direction along a rotation axis of the swing gear.

4. The rotating apparatus according to claim 1 or 2, wherein,

the crankshafts are aligned in a circumferential direction about the axis,

the stopper is located near the center of the swing gear.

5. The rotating apparatus according to claim 1 or 2, wherein,

the stopper is supported by the carrier portion.

6. The rotating apparatus according to claim 1 or 2, wherein,

an eccentric stopper engagement portion is formed in the swing gear, and the stopper is inserted into the stopper engagement portion by the stopper moving portion to stop the swing rotation.

7. The rotating apparatus according to claim 6, wherein,

the stopper moving section includes:

a pressing part which presses the stopper to be inserted into the stopper engaging part and stops the swinging rotation of the swing gear; and

and a pushing and releasing unit that releases the pushing state of the pushing unit on the stopper by the working fluid and pulls out the stopper from the stopper engaging unit.

8. The rotating apparatus according to claim 7, wherein,

the rotating device is provided with:

two bearings provided apart from each other along the axis of the housing portion, the two bearings supporting the carrier portion to the housing portion;

a supply/discharge plate having a plurality of supply/discharge channels for supplying a working fluid to a 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, the supply/discharge channels being disposed adjacent to the swing gear in the direction of the axis;

a flow path formed in the carrier portion so as to open the plurality of supply and discharge flow paths to the outside; and

a branch flow path that branches from a supply path of the flow path for supplying the working fluid to the working chamber and opens to the pushing release portion,

and releasing the pressing force of the pressing portion against the stopper by the working fluid supplied to the pressing releasing portion via the branch flow path.

9. A rotary apparatus, wherein,

the rotating device is provided with:

a housing portion having an axis;

an internal tooth provided on an inner peripheral surface of the housing portion;

a carrier portion rotatably supported by the housing portion about the axis via two bearings provided apart from each other along the axis of the housing portion;

A crankshaft rotatably supported by the carrier portion about another axis parallel to the axis and arranged in a circumferential direction about the axis;

a swing gear which is restricted to swing rotation by the crankshaft and meshes with the internal teeth;

a supply/discharge plate having a plurality of supply/discharge channels for supplying a working fluid to a 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, the supply/discharge channels being disposed adjacent to the swing gear in the direction of the axis;

a stopper supported by the carrier portion and located near the center of the swing gear, and movable in a contact-separable manner with respect to the swing gear;

a stopper engagement portion eccentrically formed on the swing gear;

a stopper moving portion that presses or releases the stopper toward the stopper engaging portion so that the stopper can be moved in a contact-separable manner toward the stopper engaging portion of the swing gear;

a flow path formed in the carrier portion so as to open the plurality of supply and discharge flow paths to the outside; and

A branch flow path that branches from a supply path of the flow path for supplying the working fluid to the working chamber and opens to the stopper moving portion,

the stopper moving portion has:

a pressing part which presses the stopper to be inserted into the stopper engaging part and stops the swinging rotation of the swing gear; and

and a pushing and releasing unit that releases the pushing state of the stopper by the pushing unit by the working fluid supplied through the branch flow path, and pulls out the stopper from the stopper engaging unit.

Images