CN116181560A - Rotary device - Google Patents

Rotary device Download PDF

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Publication number
CN116181560A
CN116181560A CN202211331721.1A CN202211331721A CN116181560A CN 116181560 A CN116181560 A CN 116181560A CN 202211331721 A CN202211331721 A CN 202211331721A CN 116181560 A CN116181560 A CN 116181560A
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CN
China
Prior art keywords
stopper
swing gear
supply
housing
axis
Prior art date
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Pending
Application number
CN202211331721.1A
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Chinese (zh)
Inventor
佐藤正隆
小森悦朗
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Nabtesco Corp
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Nabtesco Corp
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Filing date
Publication date
Priority claimed from JP2022098959A external-priority patent/JP2023079995A/en
Application filed by Nabtesco Corp filed Critical Nabtesco Corp
Publication of CN116181560A publication Critical patent/CN116181560A/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C2/00—Rotary-piston engines
    • F03C2/08—Rotary-piston engines of intermeshing-engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Transmission Devices (AREA)
  • General Details Of Gearings (AREA)
  • Hydraulic Motors (AREA)

Abstract

The present invention relates to a rotary apparatus. The rotating equipment of the invention comprises a housing part, internal teeth, a gear rack part, a crankshaft, a swinging gear, a plurality of supply and discharge flow paths, a stopper and a stopper moving part.

Description

Rotary device
Technical Field
The present invention relates to a rotary apparatus.
Background
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 for stopping the operation by restricting the swing of a swing member. As a structure of a parking brake, for example, patent document 1 discloses the following structure: the brake pin 60 in the lock position in which the swing of the star gear 30 has been suppressed is moved to the unlock position by the brake lever 72, and the lock is released.
There have been prior techniques for placing the restraining shaft into the central bore of the swing gear in this manner. Heretofore, a method of restricting the movement of the shaft and an oil passage have been improved.
Prior art literature
Patent literature
Patent document 1: japanese patent No. 5822512
Patent document 2: japanese patent No. 5288184
Disclosure of Invention
Problems to be solved by the invention
In the technique described in the patent document, the center spline shaft is made hollow, and a shaft for transmitting force to the restricting shaft is provided therein. Therefore, the construction is complicated. This causes a problem of complicating the manufacturing process.
In addition, the structure is as follows: the limiting shaft performs a precession action following the precession movement of the central spline shaft, so that the end face wears. This causes a problem of reduced durability.
The invention provides a rotary device with parking brake function, which has simple structure, high durability and miniaturization.
Solution for solving the problem
The rotating device according to an aspect of the present invention includes: 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 a stopper moving portion that presses or releases the stopper toward the swing gear to move the stopper toward the swing gear or the crankshaft in a contactable and separable manner. Thereby, the above-mentioned problems are solved.
With this configuration, the rotation of either the swing gear or the crankshaft is stopped by the stopper, and the driving of the rotating device can be stopped. In this way, the stopper is driven by the stopper moving portion, so that the stopper can be used as a brake of the rotating apparatus. Thus, a rotary apparatus having a brake mechanism that is simple and compact in construction can be provided.
In the above configuration, the stopper may press the swing gear to stop the swing rotation.
In the above configuration, the stopper moving portion may move the stopper in a direction along the rotation axis of the swing gear.
In the above configuration, the crankshafts may be arranged in a circumferential direction around the axis, and the stopper may be located near a 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 engagement portion may be formed in the swing gear, and the stopper may be inserted into the stopper engagement portion by the stopper moving portion to stop the swing rotation.
In the above configuration, the stopper moving portion may include: 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 a pushing and releasing unit that releases the pushing state of the pushing unit to the stopper by the working fluid, and pulls out the stopper from the stopper engaging unit.
In the above configuration, the rotating device may further include: 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 that supplies the working fluid to the working chamber, and that opens into the pushing release portion. The pressing force of the pressing portion against the stopper may be released by the working fluid supplied to the pressing releasing portion via the branch flow path.
A rotating device according to another aspect of the present invention includes: 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 that supplies the working fluid to the working chamber and opens into 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 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.
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, and thus the driving of the rotary device can be stopped. 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 releasing portion of the stopper moving portion via the branch flow path branched from the supply path, and the restriction of the swing gear by the stopper inserted into the stopper engaging portion by the pressing portion is released, thereby releasing the position restriction of the swing gear. In this way, the stopper is driven by the stopper moving portion, and the stopper can be used as a parking brake for braking when the driving is released and when the driving is not performed in the rotating apparatus. Thus, a rotary apparatus having a parking brake mechanism that is simple and compact in construction can be provided.
ADVANTAGEOUS EFFECTS OF INVENTION
According to the present invention, the following effects can be achieved: a rotary device having a parking brake function, which has a simple structure and high durability, and which can be miniaturized, can be provided.
Drawings
Fig. 1 is a side view partially in section showing a hydraulic motor according to embodiment 1 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 the portion III of fig. 1.
Fig. 4 is an enlarged view of a portion VI of fig. 1.
Fig. 5 is an enlarged view of the V portion showing the released state in fig. 1.
Fig. 6 is an enlarged view showing the engaged state in fig. 5.
Fig. 7 is a view corresponding to the V portion in fig. 1 of the hydraulic motor according to embodiment 2 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.
Description of the reference numerals
1. A hydraulic motor (rotating device); 2. a housing portion; 3. a rotating part; 4. a crankshaft (eccentric rotary body); 4c, an eccentric part; 5. a swing gear; 6. a carrier portion (rotating member); 7. a 1 st housing; 8. a 2 nd housing; 12. 1 st bearing (bearing); 13. a 2 nd bearing (bearing); 31. 1 st gear frame; 33b, end 2; 32. 2 nd gear carrier (gear carrier); 32d, 1 st direction end; 41. a supply path (oil path); 41g, a branch flow path; 42. a discharge path (oil path); 46. a supply/discharge plate (port plate); 50. sliding plate (piston plate); 65. external teeth; 66a, 66b, working chamber; 90. an inner tooth pin (inner tooth); 100. a braking mechanism; 100a, a stopper moving part; 101. a stopper engaging portion; 102. a stopper; 102a, a connecting member; 103. a piston; 104. 106, a cylinder; 104a, 104b, pressure chambers; 105. a spring (pressing part); c1, the 1 st axis (axis); c5, axis.
Detailed Description
Hereinafter, a rotary apparatus according to embodiment 1 of the present invention will be described with reference to the drawings.
Fig. 1 is a partially cross-sectional side view showing a hydraulic motor as an example of a rotary device in the present embodiment. Fig. 2 is a sectional view taken along line II-II of fig. 1. Fig. 3 is an enlarged view of the portion III of fig. 1. Fig. 4 is an enlarged view of section IV of fig. 1. In the drawings, reference numeral 1 is a hydraulic motor.
As the rotating device of the present embodiment, first, a hydraulic motor will be described.
< Hydraulic Motor >)
As shown in fig. 1 to 4, the hydraulic motor 1 is mainly configured by a cylindrical housing portion 2, a rotating portion 3 rotatably supported by an inner peripheral surface of the housing portion 2 via two bearings 12 and 13 (a 1 st bearing 12 and a 2 nd bearing 13), and a brake mechanism 100.
Angular contact ball bearings are used as bearings 12, 13. However, the construction of the bearings 12, 13 is not limited to angular contact ball bearings. Various bearings such as other ball bearings such as deep groove ball bearings and slide bearings may be used for the bearings 12 and 13.
The central axis of the housing part 2 coincides with the rotation axis of the rotation part 3. In the following description, these central axis and rotation axis are collectively referred to as the 1 st axis (an example of an axis in claims) C1. In some cases, the direction parallel to the 1 st axis C1 will be referred to simply as the axial direction, the rotation direction of the rotating portion 3 will be referred to simply as the circumferential direction, and the radial direction of the rotating portion 3 will be referred to simply as the radial direction.
< Shell >
The housing portion 2 is divided in the axial direction, and is constituted by a 1 st housing 7 disposed on the 1 st direction side (left side in fig. 1) in the axial direction and a 2 nd housing 8 disposed on the 2 nd direction side (right side in fig. 1) on the opposite side to the 1 st direction in the axial direction. The housing 2 may not be divided in the axial direction.
The 1 st housing 7 is formed in a cylindrical shape. An outer flange 9 protruding radially outward is formed on the outer peripheral surface 7a of the 1 st housing 7 at a position closer to the 1 st end 7b on the 1 st direction side. The outer flange 9 is used when the hydraulic motor 1 is mounted to an external device not shown. The outer flange 9 has a through hole 9a through which a bolt (not shown) passes so as to pass through the outer flange 9 in the thickness direction (axial direction).
The portion of the peripheral wall 7e of the 1 st housing 7 located between the 2 nd end 7d on the 2 nd direction side and the axial center is a thick wall portion 10 having a wall thickness thicker than that of the other portions. The 2 nd end 10c of the thick portion 10 on the 2 nd direction side is on the same plane as the 2 nd end 7d of the 1 st housing 7. That is, the 2 nd end 10c of the thick portion 10 constitutes a part of the 2 nd end 7d of the 1 st housing 7.
A plurality of (for example, 13 in the present embodiment) pin grooves 10a are formed in the inner peripheral surface 10d of the thick portion 10. The pin grooves 10a are formed in the entire thick portion 10 in the axial direction, and are arranged at equal intervals in the circumferential direction. The pin groove 10a is formed in a semicircular shape as viewed from the axial direction. A cylindrical inner tooth pin (an example of the inner tooth of the claims) 90 is rotatably accommodated in each pin groove 10a. Since the pin groove 10a is formed in a semicircular shape as viewed from the axial direction, the inner tooth pin 90 has a shape protruding from the inner peripheral surface 10d of the thick portion 10 to the radial inner side by an amount corresponding to the semicircle. The inner tooth pin 90 functions as inner teeth that mesh with the swing gear 5 discussed later.
A 1 st through hole 19 penetrating in the axial direction is formed between the pin grooves 10a in the outer peripheral portion of the thick portion 10. The 1 st through holes 19 are arranged at equal intervals in the circumferential direction. The number of the 1 st through holes 19 is 13, for example. The shaft portions 20a of bolts (an example of a fixing portion and a screw) 20 are inserted into the 1 st through holes, respectively. The 1 st housing 7, the 2 nd housing 8, and the supply and discharge plate 46 discussed later are integrally fastened together by bolts 20.
Further, a 1 st bearing housing portion 11 having a large inner diameter formed by a stepped portion 11a is formed on the inner peripheral surface 7c of the 1 st housing 7 at a position closer to the 1 st direction than the thick portion 10. The outer ring 12a of the 1 st bearing 12 is fitted into the 1 st bearing housing 11. The outer race 12a is brought into contact with the stepped portion 11a to position the 1 st bearing 12 and the 1 st housing 7.
A seal housing portion 14 having a large inner diameter formed by a stepped portion 14a is formed on the inner peripheral surface 7c of the 1 st housing 7 at a position closer to the 1 st direction than the 1 st bearing housing portion 11. A part of the seal portion 15 is fitted into the seal housing portion 14. The seal portion 15 seals between the 1 st housing 7 and the rotating portion 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 kinds of seals such as gaskets and mechanical seals can be used for the seal portion 15.
A 1 st carrier-side 1 st labyrinth portion 16 having an inner diameter larger than that of the seal housing portion 14 is formed at the 1 st end portion 7b of the 1 st shell 7. The 1 st labyrinth portion 16 on the 1 st carrier side cooperates with the rotating portion 3 to constitute a 1 st labyrinth 38. Due to the 1 st labyrinth 38, dust or the like hardly intrudes into the gap between the 1 st housing 7 and the rotating portion 3 from the outside.
The 2 nd end 7d of the 1 st housing 7 corresponds to a dividing surface between the 1 st housing 7 and the 2 nd housing 8 of the housing section 2. The entirety of the outer peripheral portion of the 2 nd end portion 7d of the 1 st housing 7 is formed flat. An O-ring groove 17, which is annular in axial direction, is formed in the outer peripheral portion of the 2 nd end portion 7d with respect to the 1 st through hole 19. An O-ring 18 is mounted in the O-ring groove 17. The O-ring 18 ensures tightness between the 1 st housing 7 and the 2 nd housing 8.
The 2 nd housing 8 is formed in a circular ring shape. A 2 nd through hole 22 communicating with the 1 st through hole 19 is formed in a position corresponding to the 1 st through hole 19 of the 1 st housing 7 in the peripheral wall 8a of the 2 nd housing 8. The 2 nd through hole 22 is formed to have the same diameter as the 1 st through hole 19, and is located on the same axis as the 1 st through hole 19. A counter bore portion 23 is formed in a majority of the 2 nd through hole 22 on the 2 nd direction side. The head 20b of the bolt 20 is inserted into the countersink region 23.
The 1 st end 8b of the 2 nd case 8 on the 1 st direction side corresponds to a dividing surface with the 1 st case 7 of the case portion 2. A pressure plate 21 protruding radially inward from the inner peripheral surface 8c of the 2 nd housing 8 is integrally formed with the 1 st end 8b of the 2 nd housing 8. The platen 21 is formed in an annular shape as viewed from the axial direction. The pressure plate 21 blocks working chambers 66a, 66b formed between an inner peripheral surface 7c of the 1 st housing 7 and an outer peripheral surface of the swing gear 5, which will be discussed later, from the 2 nd direction side.
In the case where the 1 st housing 7 and the 2 nd housing 8 are integrally formed, the pressing plate 21 can be formed separately from the housing 2.
The 2 nd carrier-side 1 st labyrinth portion 25 is formed in most part of the inner peripheral surface 21a of the platen 21 except for the end portion on the 1 st direction side. The 2 nd carrier side 1 st labyrinth portion 25 is formed by making the inner diameter larger than the inner diameter of the inner peripheral surface 21a of the platen 21 via the step portion 25 a. The 2 nd carrier-side 1 st labyrinth portion 25 cooperates with the rotating portion 3 to constitute a 2 nd labyrinth 40. Due to the 2 nd labyrinth 40, the working oil is difficult to leak from between the 2 nd casing 8 and the rotating portion 3 (details will be discussed later).
A 2 nd bearing housing portion 24 having a larger inner diameter than the pressing plate 21 via a stepped portion 24a is formed on the inner peripheral surface 8c of the 2 nd housing 8 in the 2 nd direction. The outer ring 13a of the 2 nd bearing 13 is fitted into the 2 nd bearing housing portion 24. The outer race 13a abuts against the stepped portion 24a to position the 2 nd bearing 13 and the 2 nd housing 8.
An O-ring groove 26, which is annular in axial direction, is formed in the outer peripheral portion of the 2 nd end portion 8d of the 2 nd housing 8 on the 2 nd direction side. An O-ring 27 is mounted in the O-ring groove 26. The O-ring 27 ensures tightness between the 2 nd housing 8 and a cover 29 discussed later.
At the 2 nd end 8d of the 2 nd housing 8, a plurality of female screw portions 28 are formed at equal intervals in the circumferential direction at positions radially inward of the O-ring groove 26. The cover 29 is fixed to the 2 nd housing 8 by these female screw portions 28.
< cover >
The cover 29 closes the opening 8e of the 2 nd housing 8 from the 2 nd direction side. The cover 29 is formed, for example, by press working a metal plate so that most of the center thereof bulges toward the 2 nd 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 29a overlaps the 2 nd end 8d of the 2 nd housing 8.
The outer flange 29a has a through hole 29b formed therethrough in the thickness direction at a position corresponding to the female screw portion 28 of the 2 nd housing 8. The cover 29 is fixed to the 2 nd housing 8 by inserting the bolt 30 into the through hole 29b from the 2 nd direction side and fastening the bolt 30 to the female screw portion 28 of the 2 nd housing 8.
< supply and discharge plate >)
A supply/discharge plate (port plate) 46 fixed by bolts 20 inserted into the 2 nd through holes 22 of the 2 nd housing 8 and the 1 st through holes 19 of the 1 st housing 7 is disposed at the 1 st end 10b on one side of the thick portion 10. The supply and discharge plate 46 is a plate for supplying working oil to working chambers 66a, 66b discussed later, or discharging working oil from the working chambers 66a, 66 b.
The supply/discharge plate 46 is formed in an annular shape as viewed from the axial direction. The outer diameter of the supply/discharge plate 46 is approximately equal to the diameter of the inner peripheral surface 7c of the 1 st housing 7 or slightly smaller than the diameter of the inner peripheral surface 7c of the 1 st housing 7. Accordingly, the supply/discharge plate 46 is disposed at the 1 st end 10b of the thick portion 10 so as to fit into the inner peripheral surface 7c of the 1 st housing 7.
A female screw portion 47 is formed at a position corresponding to the 1 st through hole 19 of the 1 st housing 7 on the outer peripheral portion of the supply/discharge plate 46. The bolts 20 are inserted from the 2 nd housing 8 side in the order of the 2 nd through holes 22 and the 1 st through holes 19 of the 1 st housing 7, and the bolts 20 are fastened to the female screw portions 47 of the supply/discharge plate 46. Thus, the 1 st housing 7, the 2 nd housing 8, and the supply/discharge plate 46 are fastened together by the bolts 20 to be integrated.
A plurality of through holes (supply and discharge ports) 46a penetrating in the thickness direction are formed in the supply and discharge plate 46 radially inward of the female screw portion 47. Working oil is supplied to the working chambers 66a, 66b via the through holes 46a, or working oil is discharged from the working chambers 66a, 66b (details will be discussed later). The number of through holes 46a corresponds to the number of pin grooves 10a formed in the 1 st housing 7. For example, in the present embodiment, the number of through holes 46a is 13. The through holes 46a are formed such that openings on the thick portion 10 side are located at the center between the pin grooves 10a adjacent to each other in the circumferential direction and are located radially inward of the inner peripheral surface 10d of the thick portion 10.
A plate-side labyrinth portion 48 is formed in most of the inner peripheral surface 46b of the supply/discharge plate 46 except for the end portion on the 2 nd 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 46b of the supply/discharge plate 46 via the step portion 48 a. The plate-side labyrinth portion 48 cooperates with the rotating portion 3 to constitute a 3 rd labyrinth 49. Due to the 3 rd labyrinth 49, the working oil is difficult to leak from between the supply and discharge plate 46 and the rotating portion 3 (details will be discussed later).
< rotating portion >)
The rotating portion 3 rotatably held in the housing portion 2 includes a carrier portion (rotating member) 6, a plurality of (for example, 3 in the present embodiment) crankshafts 4, and a wobble gear 5 as main components. Both axial sides of the carrier portion 6 are rotatably supported by 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 portion 6 is divided in the axial direction, and is constituted by a 1 st carrier 31 disposed on the 1 st direction side and a 2 nd carrier 32 disposed on the 2 nd direction side.
The 1 st carrier 31 has a structure in which a disk-shaped base plate portion 33 and a plurality of (for example, 3 in the present embodiment) strut portions 34 protruding in the 2 nd direction from a 2 nd end portion 33b of the base plate portion 33 on the 2 nd direction side are integrally formed.
The outer peripheral surface 33c of the base plate portion 33 is formed to have a larger outer diameter gradually from the 2 nd end portion 33b toward the 1 st end portion 33a on the 1 st direction side via the step portion.
That is, the outer peripheral surface 33c of the substrate portion 33 has, in order from the 2 nd end portion 33b side: a 1 st outer peripheral surface 33d; a 2 nd outer peripheral surface 33e formed at the 1 st direction side end of the 1 st outer peripheral surface 33d so that the outer diameter thereof becomes larger by the large step portion 33 h; a 3 rd outer peripheral surface 33f formed at the 1 st direction side end of the 2 nd outer peripheral surface 33e so that the outer diameter thereof becomes larger by the small step portion 33 i; and a 4 rd outer peripheral surface 33g formed at the 1 st direction side end of the 3 rd outer peripheral surface 33f so that the outer diameter thereof becomes larger by the intermediate step portion 33 j.
The 1 st carrier 31 is inserted into the plate-side labyrinth portion 48 of the supply/discharge plate 46 at a position corresponding to the 1 st outer peripheral surface 33 d. The outer diameter of the 1 st outer peripheral surface 33d is slightly smaller than the inner diameter of the plate-side labyrinth portion 48. The 2 nd end 33b of the 1 st carrier 31 is located slightly before the step 48a of the supply/discharge plate 46. Thus, the 3 rd labyrinth 49 is constituted by the 1 st outer peripheral surface 33d of the 1 st carrier 31, the 2 nd end 33b, and the plate-side labyrinth portion 48 of the supply/discharge plate 46.
The inner ring 12b of the 1 st bearing 12 is fitted to the 3 rd outer peripheral surface 33 f. The inner race 12b abuts against the middle step 33j to position the 1 st bearing 12 and the 1 st carrier 31. Thereby, the 1 st carrier 31 is positioned with respect to the 1 st housing 7. The 1 st carrier 31 is rotatably supported by the 1 st housing 7 via the 1 st bearing 12.
The 4 th outer peripheral surface 33g of the 1 st carrier 31 is radially opposed to the seal housing portion 14 of the 1 st housing 7. That is, the seal portion 15 is disposed between the 4 th outer peripheral surface 33g of the 1 st carrier 31 and the seal housing portion 14 of the 1 st housing 7.
A circular plate portion 35 having a circular shape as viewed from the axial direction is integrally formed at the 1 st direction side end of the 4 th outer peripheral surface 33 g. The 2 nd end 35b of the disk portion 35 on the 2 nd direction side is axially opposed to the 1 st end 7b of the 1 st casing 7. The outer diameter of the disk portion 35 is equal to the diameter of the outer peripheral surface 7a of the 1 st housing 7. A seal receiving recess 36, which is annular in axial direction, is formed in the outer peripheral portion of the 2 nd end portion 35b of the disc portion 35. The seal receiving recess 36 is smoothly continuous with the 4 th outer peripheral surface 33 g. The seal housing recess 36 also houses a part of the seal portion 15. Thereby, the 1 st housing 7 is sealed with the 1 st carrier 31 (rotating portion 3) and the seal accommodating recess 36.
A 1 st carrier-side 2 nd labyrinth portion 37 having a smaller outer diameter by a step is formed at the 2 nd end portion 35b of the disk portion 35. The 1 st labyrinth 38 is constituted by the 1 st carrier-side 2 nd labyrinth portion 37 and the 1 st carrier-side 1 st labyrinth portion 16 formed in the 1 st housing 7. Since the 1 st labyrinth 38 is disposed radially outward of the seal portion 15, intrusion of dust and the like from the outside through the gap between the 1 st housing 7 and the 1 st carrier 31 (rotating portion 3) can be reliably suppressed.
An outer flange 39 protruding radially outward is formed on the outer peripheral surface 35c of the disk 35. The outer flange 39 is used when the hydraulic motor 1 is mounted to an external device, not shown. The outer flange 39 has a through hole 39a through which a bolt (not shown) passes so as to pass through the outer flange 39 in the thickness direction (axial direction).
A plurality of (for example, 3 in the present embodiment) shaft support recesses 44 are formed at equal intervals in the circumferential direction at the 2 nd end portion 33b of the base plate portion 33 at positions closer to the outer peripheral portion (positions slightly radially inward of the 1 st outer peripheral surface 33 d). The shaft support recess 44 rotatably supports the crankshaft 4. A 1 st bearing 59a for rotatably supporting the crankshaft 4 is fitted in the shaft support recess 44. The 1 st bearing 59a is, for example, a sliding bearing. However, the configuration of the 1 st bearing 59a is not limited to the slide bearing. Various bearings such as ball bearings can be used for the 1 st bearing 59a.
Further, in the base plate portion 33, a plurality of supply paths 41, a plurality of discharge paths 42, and a drain passage (tank path) 43 are integrally formed in the axial direction of the base plate portion 33 at positions radially inward of the 2 nd outer peripheral surface 33 e.
The supply path 41 is an oil passage for supplying hydraulic oil from a hydraulic pump, not shown. The 2 nd direction side end of the supply path 41 is opened via the large step portion 33 h. That is, each supply path 41 has a supply opening 41a in the large step portion 33 h.
The discharge path 42 is an oil path for discharging the hydraulic oil in the hydraulic motor 1. The 2 nd direction side end of the discharge path 42 is also opened via the large step portion 33 h. That is, each of the discharge paths 42 has a discharge opening 42a in the large step portion 33 h.
The number of supply paths 41 and the number of discharge paths 42 are different from the number of through holes 46a of the supply/discharge plate 46 fixed to the 1 st housing 7. For example, in the present embodiment, the number of the supply paths 41 and the number of the discharge paths 42 are each 1 and 12 smaller than the number of the through holes 46a of the supply/discharge plate 46.
The supply opening 41a of the supply path 41 and the discharge opening 42a of the discharge path 42 are alternately arranged on the same pitch in the circumferential direction. The plurality of supply openings 41a and the plurality of discharge openings 42a are arranged at equal intervals in the circumferential direction so that the 1 supply opening 41a and the 1 discharge opening 42a form a pair.
The drain passage 43 is a flow path for returning the leaked hydraulic oil in the hydraulic motor 1 to a tank, not shown.
The 1 st direction side end of the supply path 41, the discharge path 42, and the drain path 43 communicates with an oil distribution portion 45 provided at the 1 st end 33a of the substrate portion 33 on the 1 st direction side. The oil distribution portion 45 has a plurality of distribution channels, not shown. Working oil from the hydraulic pump is supplied to the supply path 41 through these distribution flow paths. The hydraulic oil discharged to the discharge path 42 flows back to the tank via the distribution flow path or flows back again to the supply path 41. The hydraulic oil discharged to the drain passage 43 also flows back to the tank via the distribution passage. Further, details regarding the action of the working oil are discussed later.
A gap is formed between the large step portion 33h of the 1 st carrier 31 and the supply/discharge plate (port plate) 46. A sliding plate (piston plate) 50 is disposed in the gap. The slide plate 50 is formed in a ring shape as viewed from the axial direction. The slide plate 50 is provided so that the inner peripheral surface thereof fits to the 1 st outer peripheral surface 33d of the 1 st carrier 31, is not rotatable relative to the 1 st carrier 31, and is slidably movable in the axial direction. The thickness of the sliding plate 50 is smaller than the gap between the large step portion 33h and the supply and discharge plate 46.
The slide plate 50 has a plurality of through holes (through ports) 50c formed therein so as to correspond to the supply opening 41a of the supply path 41 and the discharge opening 42a of the discharge path 42. The through hole 50c corresponding to the supply opening 41a is disposed on the same axis as the supply opening 41 a. The through hole 50c corresponding to the discharge opening 42a is disposed on the same axis as the discharge opening 42 a.
A cylindrical piston 51 is provided in each of the supply opening 41a and the discharge opening 42 a. The piston 51 is slidably provided in the supply path 41 and the discharge path 42. The piston 51 is pressed against the slide plate 50 by a spring, not shown, provided in the supply path 41 and the discharge path 42. Thus, the piston 51 is pressed against the slide plate 50.
The thickness of the sliding plate 50 is smaller than the gap between the large step portion 33h and the supply and discharge plate 46. Therefore, the piston 51 protrudes from the large step portion 33h due to the spring and abuts against the slide plate 50. As a result, the slide plate 50 is pressed against the supply/discharge plate 46. Thus, each supply path 41 communicates with the through hole 50c of the slide plate 50 via the piston 51. The discharge paths 42 communicate with the through-hole 50c of the slide plate 50 via the piston 51. Each through hole 50c of the slide plate 50 communicates with the through hole 46a of the supply/discharge plate 46.
The strut 34 of the 1 st carrier 31 is columnar in a triangular shape as viewed from the axial direction. The support column portions 34 are arranged so as to be located between the shaft support concave portions 44 of the base plate portion 33 in the circumferential direction. That is, the pillar portions 34 are arranged at equal intervals in the circumferential direction on the 2 nd end portion 33b of the base plate portion 33. The pitch diameter of each strut portion 34 is substantially the same as the pitch diameter of the shaft support recess 44.
The distal end portion 34a of the pillar portion 34 is formed flat. The distal end 34a of the pillar 34 is flush with the 2 nd end 7d of the 1 st housing 7. A female screw portion 52 for a close-fitting bolt is formed at the distal end portion 34a of the stay portion 34.
The female screw portion 52 for the close-fitting bolt includes: a fitting recess 52a formed along the axial direction from the distal end portion 34a of the pillar portion 34 to the axial center of the pillar portion 34; and a female screw portion main body 52b extending from the bottom of the fitting recess 52a toward the 1 st direction. The 1 st carrier 31 and the 2 nd carrier 32 are integrated by fastening a tight-fit bolt (an example of another fixing portion) 53 to the tight-fit bolt with the female screw portion 52.
The 2 nd carrier 32 is formed in a disc shape. The 2 nd carrier 32 is disposed so that the 1 st end 32a on the 1 st direction side is in contact with the distal end 34a of the strut 34 constituting the 1 st carrier 31. Therefore, a gap having the same height as the pillar portion 34 is formed between the base plate portion 33 of the 1 st carrier 31 and the 2 nd carrier 32. The thick portion 10 of the 1 st housing 7 surrounds the periphery of the gap, thereby forming a swing gear housing portion 60 for housing the swing gear 5.
The 1 st end 32a of the 2 nd carrier 32 is formed flat as a whole. In the 2 nd carrier 32, fitting holes 54 penetrating in the thickness direction are formed at positions corresponding to the female screw portions 52 for the close-fitting bolts. The 1 st carrier 31 and the 2 nd carrier 32 are integrated by inserting the close-fitting bolt 53 into the fitting hole 54 from the 2 nd direction side of the 2 nd carrier 32 and fastening the close-fitting bolt 53 to the female screw portion main body 52b via the fitting recess 52a of the pillar portion 34.
The close-fit bolt 53 includes: a lever portion 53a; a male screw portion 53b protruding from a 1 st direction side end of the rod portion 53a, formed on the same axis as the rod portion 53a; and a head portion 53c formed on the same axis as the shaft portion 53a at the 2 nd direction side end of the shaft portion 53 a. In a state where the close-fitting bolt 53 is fastened to the close-fitting bolt female screw portion 52, the rod portion 53a of the close-fitting bolt 53 is fitted into the fitting recess portion 52a of the pillar portion 34 and the fitting hole 54 of the 2 nd carrier 32. That is, the shank 53a of the close-fitting bolt 53 is disposed across the 1 st carrier 31 and the 2 nd carrier 32.
A countersink 55 is formed in the fitting hole 54 at the 2 nd end 32b of the 2 nd carrier 32 on the 2 nd direction side. The head 53c of the close-fitting bolt 53 is inserted into the countersunk portion 55. Thereby, the protruding height of the head 53c of the close-fitting bolt 53 from the 2 nd end 32b of the 2 nd carrier 32 is suppressed.
The outer peripheral surface 32c of the 2 nd carrier 32 has a reduced diameter portion 56 having a smaller outer diameter formed by a stepped portion 56a in a majority of the axial center. The inner ring 13b of the 2 nd bearing 13 is fitted into the reduced diameter portion 56. Thus, the 2 nd carrier 32 is rotatably supported by the 2 nd housing 8 via the 2 nd bearing 13 with respect to the 2 nd housing 8.
A 2 nd carrier-side 2 nd labyrinth portion 57 is formed on the 1 st direction side of the portion of the reduced diameter portion 56 where the 2 nd bearing 13 is fitted. The 2 nd labyrinth portion 57 on the carrier side is formed by making the outer diameter smaller than the outer diameter of the reduced diameter portion 56 via a step portion 57 a. The outer diameter of the 2 nd carrier-side 2 nd labyrinth portion 57 is slightly smaller than the inner diameter of the 2 nd carrier-side 1 st labyrinth portion 25 of the 2 nd housing 8.
The tip end of the 2 nd carrier-side 2 nd labyrinth portion 57 is located slightly before the step portion 25a of the 2 nd carrier-side 1 st labyrinth portion 25. Thus, the 2 nd labyrinth 40 is constituted by the 2 nd carrier-side 1 st labyrinth portion 25 of the 2 nd housing 8 and the 2 nd carrier-side 2 nd labyrinth portion 57 of the 2 nd carrier 32.
A plurality of (e.g., 3 in the present embodiment) shaft support holes 58 are formed at equal intervals in the circumferential direction in the 2 nd carrier 32 at positions slightly radially inward of the 2 nd carrier-side 2 nd labyrinth portion 57. The shaft support hole 58 rotatably supports the crankshaft (eccentric rotary body) 4. These shaft support holes 58 are located on the same axis as the corresponding shaft support recesses 44 of the 1 st carrier 31. The 2 nd bearing 59b is fitted into the shaft support hole 58. The 2 nd bearing 59b is, for example, a sliding bearing. However, the configuration of the 2 nd bearing 59b is not limited to the slide bearing. Various bearings such as ball bearings can be used for the 2 nd bearing 59b.
< crankshaft >)
Each crankshaft 4 is rotatably supported by each shaft support recess 44 and the shaft support hole 58 via each bearing 59a, 59b. The crankshaft 4 can be said to slidably rotate in the shaft support recess 44 and the shaft support hole 58 via the bearings 59a, 59b.
In the present embodiment, the number of crankshafts 4 is 3. The crankshaft 4 has a structure in which bearing portions 4a and 4b (1 st bearing portion 4a and 2 nd bearing portion 4 b) rotatably supported by the shaft support recess 44 and the shaft support hole 58 via bearings 59a and 59b and a columnar eccentric portion 4c provided between the bearing portions 4a and 4b are integrally formed.
The rotation axis (2 nd axis) C2 of the crankshaft 4, that is, the axis of each bearing portion 4a, 4b is parallel to the 1 st axis C1. The movement of the crankshaft 4 in the axial direction is limited by thrust bearings 61a and 61b (1 st thrust bearing 61a and 2 nd thrust bearing 61 b) provided on the axially outer sides of the bearing portions 4a and 4b, a 1 st collar 70a provided in the shaft support recess 44 of the 1 st carrier 31, and a 2 nd collar 70b provided in the shaft support hole 58 of the 2 nd carrier 32. The movement of the 2 nd thrust bearing 61b provided in the shaft support hole 58 of the 2 nd carrier 32 out of the two thrust bearings 61a, 61b in the 2 nd direction is restricted by a retainer ring 62 provided in the shaft support hole 58.
The length of the eccentric portion 4c in the axial direction is set to be within the width of the swing gear housing portion 60 in the axial direction. Specifically, the length of the eccentric portion 4c in the axial direction is slightly shorter than the length of the thick portion 10 of the 1 st housing 7 in the axial direction. Therefore, the position of the end portion of the eccentric portion 4c on the 2 nd direction side is substantially on the same plane as the position of the 1 st end portion 8b of the 2 nd housing 8.
The axis (3 rd axis) C3 of the eccentric portion 4C is eccentric with respect to the 2 nd axis C2 of the crankshaft 4. The oscillating gear 5 is rotatably supported by the eccentric portion 4c via a 3 rd bearing 59c. The 3 rd bearing 59c is, for example, a sliding bearing. However, the configuration of the 3 rd bearing 59c is not limited to the slide bearing. Various bearings such as ball bearings can be used for the 3 rd bearing 59c.
The swing gear 5 has an outer diameter smaller than the diameter of the inner peripheral surface 10d of the thick portion 10 so as to be accommodated in the swing gear accommodating portion 60. The thickness of the swing gear 5 in the axial direction is equal to the thickness of the eccentric portion 4c in the axial direction. Thus, the position of the end portion of the swing gear 5 on the 2 nd direction side is substantially on the same plane as the position of the 1 st end portion 8b of the 2 nd housing 8. In the swing gear 5, a support hole 63 through which the eccentric portion 4c of the crankshaft 4 passes is formed at a position corresponding to the crankshaft 4.
The support holes 63 are arranged at equal intervals in the circumferential direction. The 3 rd bearing 59c is provided in these support holes 63. The movement of the wobble gear 5 in the axial direction with respect to the crankshaft 4 is restricted by the retainer rings 67 provided at both axial ends of the 3 rd bearing 59c. With such a structure, the rotation of the swing gear 5 is limited to the swing rotation by the crankshaft 4.
Further, in the swing gear 5, a relief hole 64 through which the strut 34 passes is formed at a position corresponding to the strut 34 of the 1 st carrier 31. The shape of the escape hole 64 as viewed from the axial direction is a triangular shape so as to correspond to the shape of the pillar portion 34 as viewed from the axial direction. The size of the escape hole 64 is formed to be sufficiently larger than the outer surface shape of the pillar portion 34 so that each pillar portion 34 does not interfere with the swinging rotation operation of the swing gear 5.
The outer peripheral surface of the swing gear 5 is radially opposed to the inner tooth pin 90 of the 1 st housing 7. An external tooth 65 engaged with the internal tooth pin 90 is 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 of teeth (number) of the internal teeth pins 90. For example, in the present embodiment, the number of teeth of the external teeth 65 is 12 which is 1 less than the number of teeth of the internal tooth pin 90. This number corresponds to the number of supply paths 41 and the number of discharge paths 42 formed in the 1 st carrier 31.
During the swinging rotation operation, any portion of the swing gear 5 from the tooth crest 65a to the tooth bottom 65b is always in contact with the inner tooth pin 90. Thus, two working chambers 66a and 66b (1 st working chamber 66a and 2 nd working chamber 66 b) are formed substantially between the inner peripheral surface 10d of the thick portion 10 formed in the 1 st housing 7 and the external teeth 65 of the swing gear 5. The two working chambers 66a, 66b are formed line symmetrically as viewed from the axial direction.
The plurality of through holes 46a of the supply/discharge plate (port plate) 46 communicate with the working chambers 66a, 66 b. Working oil is supplied to the working chambers 66a and 66b through the through holes 46a, and working oil is discharged from the working chambers 66a and 66 b. Thereby, the hydraulic motor 1 is rotationally driven.
Brake mechanism
Fig. 5 is an enlarged view of the 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 a parking brake thereof. The parking brake is a brake that is released and pulled up when the hydraulic motor 1 is driven.
The brake mechanism 100 includes a stopper engagement portion 101, a stopper 102, a piston 103, a cylinder 104, a spring 105, and a branch flow path 41g.
The stopper engagement portion 101 is formed penetrating through a center position of the swing gear 5. The stopper engagement portion 101 has an axis C5 parallel to the 1 st axis C1. The stopper engagement portion 101 moves around the 1 st axis C1 with the swing of the swing gear 5, and is shown as an axis C5 in fig. 5.
A cylinder 104 that opens at the 2 nd end 33b is formed in the base plate portion 33 facing the 1 st direction side of the stopper engagement portion 101. A piston 103 is housed in the cylinder 104. The cylinder 104 has an axis C5 parallel to the 1 st axis C1. The piston 103 is reciprocable inside the cylinder 104 along an axis C5 as a direction along the axis C1.
A spring (pressing portion) 105 is disposed inside the cylinder 104 on the 1 st direction side of the piston 103. The spring 105 urges the piston 103 in the 2 nd direction. Inside the cylinder 104, a branch flow passage 41g is connected to a position on the 2 nd direction side of the piston 103. The branch flow path 41g is connected to a pressure chamber 104a of the cylinder 104 on the 2 nd 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 working oil (working fluid) branched from the supply path 41 to the pressure chamber 104 a. In the pressure chamber 104a to which the hydraulic oil is supplied, the piston 103 is pressed in the 1 st direction. When the pressure of the hydraulic oil supplied from the pressure chamber 104a to the piston 103 is greater than the urging force of the spring 105, the piston 103 moves in the 1 st direction.
When the pressure of the hydraulic oil applied to the piston 103 from the pressure chamber 104a is smaller than the urging force of the spring 105, and when the hydraulic oil is not supplied to the pressure chamber 104a, the piston 103 is movable in the 2 nd direction due to the urging force of the spring 105.
The 2 nd direction end portion of the piston 103 is formed as a stopper 102 so as to have the same diameter as that of the stopper engaging portion 101. The stopper 102 and the stopper engaging portion 101 have the same cross-sectional shape. The stopper 102 and the stopper engaging portion 101 may have a circular cross-sectional shape or a polygonal cross-sectional shape.
The stopper 102 moves in a contact-capable and separation-capable manner along the axis C5 with respect to the swing gear 5 with the reciprocating action of the piston 103. The stopper 102 is protruded from the 2 nd end 33b of the base plate 33 toward the 2 nd direction due to the urging force of the spring 105. When the stopper 102 moves in the 2 nd 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, there is a case where the positions of the stopper 102 and the stopper engaging portion 101 are not aligned, but the positions of the stopper 102 and the stopper engaging portion 101 are always aligned during one rotation of the output of the carrier portion 6. When the stopper 102 is aligned with the stopper engaging portion 101, the stopper 102 is inserted into the stopper engaging 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.
Before the hydraulic oil is supplied to the pressure chamber 104a, the stopper 102 is inserted into the stopper engagement portion 101 due to the urging force of the spring 105. When the hydraulic oil is supplied to the pressure chamber 104a through the branch flow path 41g, the force generated by the stopper 102 due to the hydraulic oil becomes larger than the urging force of the spring 105. Thereby, the stopper 102 presses the piston 103 in the 1 st direction. When the piston 103 moves in the 1 st direction, the stopper 102 moves in the 1 st direction and is pulled out from the stopper engaging portion 101. The stopper 102 separated from the swing gear 5 is located closer to the 1 st direction than the 2 nd end 33b of the base plate 33, and is housed in the cylinder 104.
The spring 105, the piston 103 and the cylinder 104 as the pushing canceling portions, and the branch flow path 41g constitute a stopper moving portion 100a.
< action of Hydraulic Motor >)
Hereinafter, the operation of the hydraulic motor 1 will be discussed 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 66a and 66b via the piston 51 of each supply opening 41a, the through hole 50c of the slide plate 50, and the through hole 46a of the supply/discharge plate (port plate) 46.
The piston 51 of each supply opening 41a slides on the slide plate 50 integrally rotated with the 1 st carrier 31 while being pressed against the slide plate 50 by a spring. When the through hole 50c reaches a position aligned with the piston 51 due to 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 integrally rotated with the 1 st carrier 31 slides with respect to the supply/discharge plate (port plate) 46 integrally provided with the housing portion 2. When the through hole 46a reaches a position aligned with the through hole 50c due to 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 46 a.
When the through hole 46a and the through hole 50c are not aligned and are not in communication, the through hole 46a is blocked by the slide plate 50. This prevents the working oil from leaking from the working chambers 66a and 66b through the through holes 46a or flowing backward.
The number of the supply paths 41 (the supply opening 41a and the through holes 50c of the slide plate 50 communicating with the supply opening 41 a) is 1 less than the number of the through holes 46a of the supply/discharge plate 46. The number of the discharge paths 42 (the discharge openings 42a and the through holes 50c of the slide plate 50 communicating with the discharge openings 42 a) is 1 smaller than the number of the through holes 46a of the discharge plate 46. Therefore, only the supply path 41 is connected to either one of the two working chambers 66a and 66b via the through hole 46a of the supply/discharge plate 46. In addition, only the discharge path 42 communicates with the other of the two working chambers 66a, 66b through the through hole 46a of the supply/discharge plate 46.
Then, the pressure inside any one of the two working chambers 66a, 66b is higher than the pressure inside any other one of the two working chambers 66a, 66b. In order to make the description easier, a case will be described in which the pressure of the working chamber 66a (left side in fig. 2) is higher than the pressure of the working chamber 66b (right side in fig. 2) among the two working chambers 66a, 66b. In the following description, the high-pressure working chamber 66a 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 referred to as a low-pressure working chamber 66b. The high-pressure working chamber 66a communicates with the supply path 41. The low-pressure working chamber 66b communicates with the discharge path 42.
By supplying the working 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 hydraulic oil in the low-pressure working chamber 66b 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 low pressure working chamber 66b side. Then, since the number of teeth of the external teeth 65 is 1 less than the number of teeth of the internal teeth pin 90, the swing gear 5 is slightly deviated in the rotation direction.
At this time, the carrier portion 6 is deviated in the rotation direction along with the swing gear 5 by the crankshaft 4. That is, the rotating portion 3 slightly rotates with respect to the housing portion 2. Thus, the slide plate 50 rotates relative to the supply and discharge plate 46. Then, the state is switched in which the through hole 50c of the slide plate 50 communicates with the through hole 46a of the supply/discharge plate 46. Since the swing gear 5 swings and rotates, the high-pressure working chamber 66a is also slightly deviated in the rotation direction with respect to the low-pressure working chamber 66b.
When the state in which the through hole 50c of the slide plate 50 and the through hole 46a of the supply/discharge plate 46 communicate with each other is switched, the hydraulic oil is supplied again to the high-pressure working chamber 66 a. In addition, the hydraulic oil is discharged from the low-pressure working chamber 66 b. By repeating this operation in sequence, the rotary part 3 rotates with respect to the housing part 2. The output is obtained using this rotation.
When the through hole 46a reaches a position aligned with the through hole 50c due to rotation of the slide plate 50 and the supply/discharge plate 46, hydraulic oil is discharged from the low-pressure working chamber 66b to the through hole 50 c.
When the through hole 46a and the through hole 50c are not aligned and are not in communication, the through hole 46a is closed by the slide plate 50, and the hydraulic oil is prevented from being discharged from the working chambers 66a and 66b through the through hole 46 a.
The piston 51 of the discharge opening 42a of the discharge path 42 slides with respect to the slide plate 50 integrally rotated with the 1 st carrier 31 in a state of being pressed against the slide plate 50 by a spring. When the through hole 50c reaches a position aligned with the piston 51 due to the rotation of the slide plate 50, the hydraulic oil discharged from the through hole 46a is discharged to the discharge path 42 via the piston 51 of the discharge opening 42 a. The hydraulic oil discharged to the discharge path 42 flows back to the tank via the distribution flow path.
In this way, the hydraulic motor 1 sequentially switches the states in which the number of the supply paths 41 (the supply opening 41a and the through holes 50c of the slide plate 50 communicating with the supply opening 41 a) and the number of the through holes 46a of the supply/discharge plate 46 are not identical, and the number of the discharge paths 42 (the discharge opening 42a and the through holes 50c of the slide plate 50 communicating with the discharge opening 42 a) and the number of the through holes 46a of the supply/discharge plate 46 are not identical, in the circumferential direction, so that the through holes 50c of the slide plate 50 and the through holes 46a of the supply/discharge plate 46 are communicated. As a result, the 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 rotating portion 3 rotates.
The carrier 6 constituting the rotating portion 3 is divided into a 1 st carrier 31 and a 2 nd carrier 32. Since the 1 st carrier 31 and the 2 nd carrier 32 are fixed by the close-fitting bolts 53, power transmission between the 1 st carrier 31 and the 2 nd carrier 32 is performed by the close-fitting bolts 53. The shank 53a of the close-fitting bolt 53 is disposed across the 1 st carrier 31 and the 2 nd carrier 32. Therefore, compared with the case where the male screw portion 53b spans between the 1 st carrier 31 and the 2 nd carrier 32, the power transmission between the 1 st carrier 31 and the 2 nd carrier 32 is performed efficiently.
The 3 rd labyrinth 49 is formed by the 1 st outer peripheral surface 33d of the 1 st carrier 31, the 2 nd end 33b, and the plate-side labyrinth portion 48 of the supply/discharge plate 46 on the 1 st direction side of the swing gear 5. On the 2 nd direction side of the swing gear 5, the 2 nd labyrinth 40 is constituted by the 2 nd carrier side 1 st labyrinth portion 25 of the 2 nd housing 8 and the 2 nd carrier side 2 nd labyrinth portion 57 of the 2 nd carrier 32. Therefore, the working oil leaking from the working chambers 66a, 66b through the small gap between the crankshaft 4 and the swing gear 5 is less likely to leak from between the 1 st housing 7 and the 1 st carrier 31 and between the 2 nd housing 8 and the 2 nd carrier 32.
In the hydraulic motor 1, the housing portion 2 is fixed, whereby an output from the rotating portion 3 can be obtained. In this case, the external device fixed to the outer flange 39 of the rotating portion 3 (1 st carrier 31) becomes a rotated body. Further, by fixing the rotating portion 3, output can also be obtained from the housing portion 2. In this case, the external device fixed to the outer flange 9 of the housing 2 (1 st housing 7) becomes a rotated body.
The hydraulic motor 1 has an inner tooth pin 90 provided in the 1 st housing 7. The rotating unit 3 includes: a carrier portion 6; a crankshaft 4 rotatably supported by the carrier portion 6; and a swing gear 5 which is restricted to swing rotation by the crankshaft 4 and meshes with the internal tooth pin 90. With this configuration, the hydraulic motor 1 can be driven to rotate by supplying or discharging the hydraulic oil to or from the working chambers 66a and 66b formed between the inner peripheral surface 7c of the 1 st housing 7 and the outer peripheral surface of the swing gear 5. A high torque can be obtained with this rotational drive. The housing 2 formed by dividing can be preferably used for the hydraulic motor 1.
The hydraulic motor 1 has a supply/discharge plate 46 for selectively supplying and discharging hydraulic oil to and from the respective working chambers 66a and 66 b. The supply/discharge plate 46 is disposed at the 1 st end 10b (1 st direction side end of the swing gear 5) of the thick portion 10. Such a supply and discharge plate 46 is fixed to the 1 st housing 7 by bolts 20. The supply and discharge plate 46 is also fixed by bolts 20 for fixing the 1 st housing 7 and the 2 nd housing 8.
In the hydraulic motor 1, when the 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 104 a.
In a state where the hydraulic oil is not supplied from the hydraulic pump, the hydraulic oil is not supplied to the pressure chamber 104 a. Accordingly, in the brake mechanism 100, the piston is pressed in the 2 nd direction by the pressing 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. Thus, 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 the hydraulic oil is supplied to the pressure chamber 104a, the pressure of the hydraulic oil in the pressure chamber 104a becomes higher than the urging force of the spring 105, and the piston 103 moves in the 1 st direction. Then, as shown in fig. 5, the stopper 102 is pulled out from the stopper engagement 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.
The supply of the hydraulic oil to the pressure chamber 104a may be a supply of a hydraulic pump for driving the hydraulic motor 1 that supplies the hydraulic oil to the working chambers 66a and 66b, or may be another pilot pressure.
As described above, in the above-described embodiment, the brake mechanism 100 can be operated as a parking brake by the stopper moving portion 100a, and the stopper moving portion 100a uses the spring 105 and the hydraulic oil used for driving the hydraulic motor 1. In this way, in the so-called cycloid-type hydraulic motor 1 using the swing gear, the crankshaft 4 and the stopper 102 can be configured as separate members. Thus, the crankshaft 4 and the stopper 102 can be prevented from performing a unified operation such as integrally rotating. Therefore, the resistance to the driving of the hydraulic motor 1 can be reduced, and the energy consumption can be reduced. Further, as an effect thereof, it is possible to provide at low cost by a simple structure in which only the stopper 102 that reciprocates by the cylinder 104, the piston 103, and the spring 105 provided in the base plate portion 33 is advanced and retracted with respect to the stopper engaging portion 101 provided in the swing gear 5.
Further, the stopper 102 driven by the cylinder 104, the piston 103, and the spring 105 provided in the base plate 33 can be advanced and retracted with respect to the stopper engaging portion 101 provided in the swing gear 5, thereby achieving a compact structure. A simple structure can be realized that advances and retreats relative to the stopper engagement portion 101 provided in the swing gear 5, and therefore, the processing is easy. Since the cylinder 104 and the piston 103 are provided in the base plate 33, the branch flow passage 104g for supplying the hydraulic oil for releasing the brake is easily formed. Further, since the substrate portion 33 is a portion that does not rotate, a flow path can be easily formed. Further, since the brake-driving hydraulic oil can be supplied to the cylinder 104 by forming one branch flow passage 41g, space saving can be achieved.
Further, the crankshaft 4, the cylinder 104, and the piston 103 can be easily arranged. Further, since the stopper 102 can be braked only by the operation of inserting the stopper 102 into the stopper engaging portion 101, the stopper can be operated without fear of tilting between the stopper 102 and the stopper engaging portion 101. Thus, a reliable braking operation can be realized with the number of components reduced.
Hereinafter, a rotary apparatus according to embodiment 2 of the present invention will be described with reference to 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 the present 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. The present embodiment is different from embodiment 1 described above in relation to the stopper moving portion. The same reference numerals are given to the structures corresponding to embodiment 1 above except for the stopper moving portion, and the description thereof will be omitted.
As shown in fig. 7, the stopper moving portion 100a of the present embodiment includes a cylinder 106 formed in the 2 nd carrier 32. The cylinder 106 is opened on the 1 st direction side so as to face the swing gear 5. The cylinder 106 has a communication port on the 2 nd direction side facing the cover 29. Inside the cylinder 106, a stopper 102 is housed on the 1 st direction side. The cylinder 106 may also 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 reciprocable inside the cylinder 106 along an axis C5 as a direction along the axis C1.
Inside the cylinder 106, a spring 105 is disposed on the 2 nd direction side of the stopper 102. The spring 105 urges the stopper 102 toward the 1 st direction.
The stopper 102 is connected to a coupling member 102a along the axis C5 on the 1 st direction side. The coupling member 102a is connected coaxially with the axis C5 of the stopper 102. The connecting member 102a is connected to a piston 103 at an end portion on the 1 st direction side. The stopper 102, the coupling member 102a, and the piston 103 are integrally movable in a direction along the axis C5. The coupling member 102a is disposed inside the stopper engaging portion 101. The coupling member 102a has a diameter smaller than that of the stopper engaging portion 101. Even if the swing gear 5 swings and rotates, the coupling member 102a does not contact the stopper engagement portion 101.
The piston 103 is accommodated in the cylinder 104. The cylinders 104 and 106 are disposed coaxially with each other on both sides of the swing gear 5 in the thickness direction. The cylinder 104 on the 1 st direction side of the swing gear 5 and the cylinder 106 on the 2 nd direction side of the swing gear 5 are formed as cylinders continuous in the axis C5 direction. That is, the cylinder 104 and the cylinder 106 are formed in the carrier portion 6.
Inside the cylinder 104, a branch flow passage 41g is connected to a position on the 1 st direction side of the piston 103. The branch flow path 41g is connected to a pressure chamber 104b of the cylinder 104 on the 1 st 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 working oil branched from the supply path 41 to the pressure chamber 104 b. In the pressure chamber 104b supplied with the hydraulic oil, the piston 103 is pressed in the 2 nd direction. When the pressure of the hydraulic oil from the pressure chamber 104b applied to the piston 103 is greater than the pressing force of the spring 105 of the cylinder 106 to press the stopper 102 in the 1 st direction, the piston 103 and the stopper 102 move in the 2 nd direction.
The stopper 102 is movable in a contact-separable manner along the axis C5 with respect to the swing gear 5 integrally with the coupling member 102a and the piston 103. The stopper 102 is protruded from the 1 st direction end 32d of the 2 nd carrier 32 toward the 1 st direction due to the urging force of the spring 105. When the stopper 102 moves in the 1 st 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, there is a case where the positions of the stopper 102 and the stopper engaging portion 101 are not aligned, but the positions of the stopper 102 and the stopper engaging portion 101 are always aligned during one rotation of the output of the carrier portion 6. When the stopper 102 is aligned with the stopper engaging portion 101, the stopper 102 is inserted into the stopper engaging 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.
Before the hydraulic oil is supplied to the pressure chamber 104b, the stopper 102 is inserted into the stopper engagement portion 101 due to the urging force of the spring 105. When the hydraulic oil is supplied to the pressure chamber 104b through the branch flow path 41g, the force generated by the stopper 102 by the action of the hydraulic oil becomes larger than the urging force of the spring 105. Thereby, the stopper 102 presses the piston 103 in the 2 nd direction. When the piston 103 moves in the 2 nd direction, the stopper 102 integrated with the coupling member 102a moves in the 2 nd direction and is pulled out from the stopper engaging portion 101. The stopper 102 separated from the swing gear 5 is located closer to the 2 nd direction than the 1 st direction end 32d of the 2 nd carrier 32, and is housed in the cylinder 106.
In the present embodiment, the hydraulic motor 1 supplies hydraulic oil to the working chambers 66a and 66b via the supply path 41 from a hydraulic pump, not shown. Thereby, the swing gear 5 is slightly deviated in the rotation direction due to the working oil supplied to the working chambers 66a, 66b, and a rotation output is obtained. At the same time, the hydraulic oil is supplied from the supply path 41 to the pressure chamber 104b via the branch flow path 41 g.
In a state where the hydraulic oil is not supplied from the hydraulic pump, the hydraulic oil is not supplied to the pressure chamber 104 b. Accordingly, in the brake mechanism 100, the piston is pressed in the 1 st direction by the pressing 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. Thus, 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 the hydraulic oil is supplied to the pressure chamber 104b, the pressure of the hydraulic oil in the pressure chamber 104b becomes higher than the urging force of the spring 105, and as shown in fig. 7, the piston 103 moves in the 2 nd direction. 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.
The supply of the hydraulic oil to the pressure chamber 104b may be a supply of a hydraulic pump for driving the hydraulic motor 1 that supplies the hydraulic oil to the working chambers 66a and 66b, or may be another pilot pressure.
In the present embodiment, the brake mechanism 100 can be operated as a parking brake by the stopper moving portion 100a, and the stopper moving portion 100a uses the spring 105 and the hydraulic oil used for driving the hydraulic motor 1. This can provide effects equivalent to those of the above-described embodiments.
Further, since the cylinder 106 is formed in the 2 nd carrier 32, a space for accommodating the spring 105 does not need to be formed in the cylinder 104 of the base plate portion 33. Meanwhile, the pressure chamber 104a does not need to be formed on the 2 nd direction side of the piston 103. Therefore, the space of the substrate 33 can be reduced.
In the above embodiments, the rotation of the swing gear 5 is stopped by the stopper 102, but the object of stopping the rotation by the stopper may be the crankshaft 4 as the brake mechanism 100. In this case, the crankshaft 4 is preferably located at the center of the swing gear 5.
In the above embodiments, the stopper engagement portion 101 is formed so as to penetrate the swing gear 5, but may be formed as a recess in which the stopper 102 is engaged, and may not penetrate.
Alternatively, the following structure may be employed: the stopper 102 contacts the swing gear 5 or the crankshaft 4 to press them, thereby stopping the rotation.
In the embodiments disclosed in the present specification, a plurality of objects may be integrated with a member composed of a plurality of objects, and conversely, a member composed of one object may be divided into a plurality of objects. Whether or not integrated, the present invention may be constructed so as to achieve the object of the present invention.

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.
CN202211331721.1A 2021-11-29 2022-10-28 Rotary device Pending CN116181560A (en)

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JP2021-193136 2021-11-29
JP2021193136 2021-11-29
JP2022098959A JP2023079995A (en) 2021-11-29 2022-06-20 Rotary equipment
JP2022-098959 2022-06-20

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Publication number Priority date Publication date Assignee Title
JPS5288184U (en) 1975-12-25 1977-07-01
JPS5822512B2 (en) * 1980-11-07 1983-05-09 川崎製鉄株式会社 Coal liquefied solidification equipment
JPS5853450Y2 (en) 1981-08-07 1983-12-05 千英 赤星 wheel shaft
US8500423B2 (en) * 2010-04-13 2013-08-06 Eaton Corporation Frame rotated hydraulic motor with improved parking brake
JP5782321B2 (en) * 2011-07-15 2015-09-24 ナブテスコ株式会社 Gear device

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