JP2023079596A - Rotating apparatus and method for assembling rotating apparatus - Google Patents

Abstract

To provide a rotating apparatus that can be readily assembled, and to provide a method for assembling a rotating apparatus.SOLUTION: A hydraulic motor 1 includes: a housing part 2 comprising a first housing 7 and a second housing 8 split in an axial direction; a rotary part 3 supported to the housing part 2 so as to be freely rotatable about an axis line via two bearings 12, 13 installed on both sides while interposing parting plane of the housing part 2 therebetween; and a bolt 20 for fixing the first housing 7 and the second housing 8 while imparting preload to the two bearings 12, 13.SELECTED DRAWING: Figure 1

Description

TECHNICAL FIELD The present invention relates to a rotating device and a method for assembling a rotating device.

As a rotary device, there is a speed reduction device that reduces the speed of input rotation and outputs the speed. The speed reducer includes a cylindrical housing having internal teeth formed on the inner peripheral surface, a carrier rotatably supported by the housing via a bearing, a crankshaft rotatably supported by the carrier, and a crankshaft. and an oscillating gear that is oscillatingly rotated by the oscillating gear and meshed with the internal teeth.
In this type of speed reducer, rotation of a motor or the like is input to a crankshaft. Output is then obtained from a carrier or housing that is rotated via the oscillating gear. That is, when the carrier is fixed, the output can be obtained from the housing. On the other hand, if the housing is fixed, the output can be obtained from the carrier.

JP 2016-65574 A

Bearings for rotatably supporting the carrier with respect to the housing are often provided at both axial ends of the carrier. To efficiently rotate the carrier with respect to the housing, it is important to improve the concentricity of the two bearings. For this reason, it is necessary to perform high-precision processing such as simultaneous processing on each portion of the housing where the two bearings are fitted, and then assemble the bearings. As a result, there is a problem that the number of man-hours for assembling the rotating device increases.

The present invention provides a rotating device that can be easily assembled and a method for assembling the rotating device.

A rotating device according to an aspect of the present invention includes a housing portion composed of a first housing and a second housing divided in an axial direction, bearings respectively provided in the first housing and the second housing, and each of the bearings. a rotating portion supported by the housing portion so as to be rotatable about the axis, and a fixing portion for fixing the first housing and the second housing in a state in which a preload is applied to each of the bearings. Prepare.

In this way, the housing section is divided into the first housing and the second housing. Since the two bearings that rotatably support the rotating portion are provided on both sides of the divided surface of the housing portion, two bearings are separately provided in each housing. With such a configuration, positional adjustment (centering) of the two bearings can be performed by applying a preload to each bearing and adjusting the positions of the first housing and the second housing. That is, there is no need to apply high-precision processing such as simultaneous processing to each portion of the housing portion where the two bearings are fitted. As a result, assembly of the rotating device can be facilitated.

In the above configuration, the fixing portion may be a screw.

In the above configuration, the entire dividing surface of the housing portion may be flat.

In the above configuration, the inner teeth are provided on the inner peripheral surface of the housing portion, and the rotating portion includes a carrier rotatably supported by the housing portion via the two bearings, and the It may have a crankshaft rotatably supported around another axis parallel to the axis, and an oscillating gear that is restricted from oscillating rotation by the crankshaft and meshed with the internal teeth.

In the above configuration, a supply and discharge plate for supplying hydraulic oil between the inner peripheral surface of the housing portion and the oscillating gear and for discharging hydraulic oil from between the inner peripheral surface of the housing portion and the oscillating gear. The supply/discharge plate may be disposed at one end of the oscillating gear in the axial direction and fixed to the housing portion by the fixing portion.

A rotating device according to another aspect of the present invention includes a housing portion composed of a first housing and a second housing divided in an axial direction and each having a flat dividing surface; inner teeth, bearings respectively provided in the first housing and the second housing, a carrier rotatably supported by the housing portion around the axis through each of the bearings, and the carrier and the axis. A crankshaft rotatably supported around another parallel axis, an oscillating gear that is regulated to oscillating rotation by the crankshaft and meshed with the internal teeth, and a preload applied to each of the bearings. A screw for fixing the first housing and the second housing, supplying hydraulic oil between the inner peripheral surface of the first housing and the oscillating gear, and supplying hydraulic oil between the inner peripheral surface of the first housing and the oscillating gear. a supply/drainage plate for discharging hydraulic oil from between the gear and the gear, the supply/drainage plate being arranged at the first housing side end of the oscillating gear in the axial direction, and being screwed by the screw; 1 housing.

In this way, the housing section is divided into the first housing and the second housing. Since the two bearings that rotatably support the rotating portion are provided on both sides of the divided surface of the housing portion, two bearings are separately provided in each housing. With such a configuration, positional adjustment (centering) of the two bearings can be performed by applying a preload to each bearing and adjusting the positions of the first housing and the second housing. That is, there is no need to apply high-precision processing such as simultaneous processing to each portion of the housing portion where the two bearings are fitted. As a result, assembly of the rotating device can be facilitated.
Further, after the first housing and the second housing are temporarily tightened with screws, the positions of the first housing and the second housing can be adjusted. After that, by further tightening, each housing can be reliably fixed while suppressing the positional deviation of each housing.
Furthermore, a high reduction ratio can be obtained as a rotating device, and the rotating device can be used as a hydraulic motor. And it can be suitably used for a rotating device capable of obtaining such a high speed reduction ratio. The housing portion and the supply/discharge plate can be integrated by using the fixing portion that fixes the first housing and the second housing.

According to another aspect of the present invention, there is provided a method of assembling a rotating device, comprising: a housing portion composed of a first housing and a second housing divided in an axial direction; a first bearing provided in the first housing; a second bearing provided in a housing; a rotating portion supported by the housing portion through the first bearing and the second bearing so as to be rotatable about the axis; the first housing and the second housing; a first bearing assembly step of assembling the first bearing to either the first housing or the rotating portion; After the second bearing assembling step of assembling the second bearing to one of the rotating parts, and the first bearing assembling step and the second bearing assembling step, the first bearing is attached to the first housing and the second housing. and a rotating portion assembling step of assembling the rotating portion via the second bearing; a preloading step of applying preload to the first bearing and the second bearing after the rotating portion assembling step; and the preloading step. and a housing fixing step of fixing the first housing and the second housing by the fixing portion.

By adopting such an assembling method, positional adjustment (centering) of the first bearing and the second bearing can be easily performed. Therefore, assembly of the rotary device can be facilitated.

In the above configuration, the rotating part is rotatably supported by a first carrier rotatably supported by the first housing via the first bearing, and rotatably supported by the second housing via the second bearing. and a second carrier, and the first carrier and the second carrier may be fixed by another fixing part in the rotating part assembling step.

The rotating equipment described above can be easily assembled.

1 is a partial cross-sectional side view of a hydraulic motor according to an embodiment of the present invention; FIG. FIG. 2 is a cross-sectional view taken along line II-II of FIG. 1; FIG. 2 is an enlarged view of part III of FIG. 1; FIG. 2 is an enlarged view of part IV of FIG. 1; It is an explanatory view for explaining a method of assembling the hydraulic motor in the embodiment of the present invention.

Next, embodiments of the present invention will be described based on the drawings.

<Hydraulic motor>
FIG. 1 is a partial cross-sectional side view of the hydraulic motor 1. FIG. FIG. 2 is a cross-sectional view along line II-II of FIG. FIG. 3 is an enlarged view of section III in FIG. FIG. 4 is an enlarged view of part IV in FIG.
As shown in FIGS. 1 to 4, a hydraulic motor 1, which is a rotary device, includes a cylindrical housing portion 2 and two bearings 12 and 13 (a first bearing 12 and a second bearing) on the inner peripheral surface of the housing portion 2. 13), which is rotatably supported via the rotor 3).
Angular ball bearings are used as the bearings 12 and 13 . However, it is not limited to this, and it is also possible to use a tapered roller bearing.

The center axis of the housing portion 2 and the rotation axis of the rotating portion 3 are aligned. In the following description, these central axis and rotation axis are collectively referred to as a first axis (an example of an axis in the claims) C1. In some cases, the direction parallel to the first axis C1 is simply referred to as the axial direction, the rotating direction of the rotating portion 3 is referred to as the circumferential direction, and the radial direction of the rotating portion 3 is simply referred to as the radial direction.

<Housing part>
The housing portion 2 is divided in the axial direction into a first housing 7 arranged on the axial first direction side (the left side in FIG. 1) and a second axial direction side opposite to the first axial direction (the left side in FIG. 1). a second housing 8 arranged on the right side in FIG. 1).
The first housing 7 is formed in a cylindrical shape by casting, for example. An outer flange portion 9 projecting radially outward is formed on the outer peripheral surface 7a of the first housing 7 near the first end portion 7b on the first direction side. The outer flange portion 9 is for attaching the hydraulic motor 1 to an external device (not shown). The outer flange portion 9 is formed with through-holes 9a through which bolts (not shown) pass through in the thickness direction (axial direction) of the outer flange portion 9 .

A portion of the peripheral wall 7e of the first housing 7 from the second end 7d on the second direction side to the center in the axial direction forms a thick portion 10 that is thicker than other portions. A second end portion 10 c of the thick portion 10 on the second direction side is positioned on the same plane as the second end portion 7 d of the first housing 7 . That is, the second end portion 10c of the thick portion 10 forms part of the second end portion 7d of the first housing 7. As shown in FIG.

A plurality of (for example, 13 in this embodiment) pin grooves 10a are formed in the inner peripheral surface 10d of the thick portion 10 . Each pin groove 10a is formed in the entire thick portion 10 along the axial direction and is arranged at equal intervals in the circumferential direction. The pin groove 10a is formed in a semicircular shape when viewed from the axial direction. Each pin groove 10a rotatably accommodates a cylindrical internal tooth pin (an example of internal teeth in the claims) 90 . The internal pin 90 is made of high-carbon chromium bearing steel or the like that is generally used in bearings and the like. Since the pin groove 10a is formed in a semicircular shape when viewed in the axial direction, the internal pin 90 protrudes radially inward from the inner peripheral surface 10d of the thick portion 10 by a semicircular portion. The internal pin 90 functions as an internal tooth that meshes with the oscillating gear 5, which will be described later.

A first through hole 19 is formed in the outer peripheral portion of the thick portion 10 so as to penetrate in the axial direction between the pin grooves 10a. The first through holes 19 are arranged at regular intervals in the circumferential direction. The number of the first through holes 19 is eight, for example. A shaft portion 20 a of a bolt (an example of a fixing portion and a screw in the claims) 20 is inserted into these first through holes 19 . The bolts 20 fasten together the first housing 7, the second housing 8, and a supply/discharge plate 46, which will be described later, to integrate them.

A first bearing accommodating portion 11 having a large inner diameter is formed on the inner peripheral surface 7c of the first housing 7, closer to the first direction than the thick portion 10 via a stepped portion 11a. An outer race 12 a of a first bearing 12 is fitted into the first bearing housing portion 11 . Positioning between the first bearing 12 and the first housing 7 is performed by bringing the outer race 12a into contact with the stepped portion 11a.

In the inner peripheral surface 7c of the first housing 7, a seal storage portion 14 having a large inner diameter is formed nearer to the first direction than the first bearing storage portion 11 via a stepped portion 14a. A portion of the seal portion 15 is fitted into the seal housing portion 14 . The seal portion 15 seals between the first housing 7 and the rotating portion 3 . A floating seal, for example, is used as the seal portion 15 . However, it is not limited to this, and various seals such as packings and mechanical seals can be used.

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 carrier-side first labyrinth portion 16 forms a first labyrinth 38 in cooperation with the rotating portion 3 . The first labyrinth 38 makes it difficult for dust and the like to enter between the first housing 7 and the rotating portion 3 from the outside.

A second end portion 7 d of the first housing 7 corresponds to a dividing surface between the first housing 7 and the second housing 8 of the housing portion 2 . The second end portion 7d of the first housing 7 has a flat outer peripheral portion. An annular O-ring groove 17 is formed in the second end portion 7d closer to the outer peripheral portion than the first through hole 19 when viewed from the axial direction. An O-ring 18 is mounted in 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 by casting, for example. A second through hole 22 communicating with the first through hole 19 of the first housing 7 is formed in the peripheral wall 8 a of the second housing 8 at a position corresponding to the first through hole 19 of the first housing 7 . The second through hole 22 is formed with the same diameter as the first through hole 19 and is positioned coaxially with the first through hole 19 . A counterbore 23 is formed in most of the second direction side of the second through hole 22 . The head portion 20 b of the bolt 20 is inserted into the counterbore portion 23 .

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

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

A second bearing accommodating portion 24 having a large inner diameter is formed on the inner peripheral surface 8c of the second housing 8, closer to the second direction than the pressing plate 21, with a stepped portion 24a interposed therebetween. The outer race 13 a of the second bearing 13 is fitted into the second bearing housing portion 24 . The positioning of the second bearing 13 and the second housing 8 is performed by the contact of the outer race 13a against the stepped portion 24a.

An annular O-ring groove 26 is formed in the outer peripheral portion of the second end portion 8d on the second direction side of the second housing 8 when viewed from the axial direction. An O-ring 27 is mounted in the O-ring groove 26 . The O-ring 27 ensures sealing between the second housing 8 and a cover 29 which will be described later.
A plurality of female threaded portions 28 are formed radially inward of the O-ring groove 26 at the second end portion 8d of the second housing 8 at regular intervals in the circumferential direction. These female threaded portions 28 are for fixing the cover 29 to the second housing 8 .

<Cover>
The cover 29 closes the opening 8e of the second housing 8 from the second direction side. The cover 29 is formed, for example, by pressing a metal plate so that most of the central part bulges toward the second direction. An outer peripheral portion of the cover 29 is formed with an outer flange portion 29a. The outer flange portion 29 a overlaps the second end portion 8 d of the second housing 8 .

A through hole 29b is formed through the outer flange portion 29a in the thickness direction at a position corresponding to the female threaded portion 28 of the second housing 8 . The cover 29 is fixed to the second housing 8 by inserting the bolt 30 into the through hole 29 b from the second direction side and tightening the bolt 30 to the female threaded portion 28 of the second housing 8 .

<Supply and exhaust plate>
A supply/discharge 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 attached to the first end 10 b of the thick portion 10 . are placed in The supply/discharge plate 46 is a plate for supplying hydraulic oil to working chambers 66a and 66b, which will be described later, and for discharging working oil from the working chambers 66a and 66b.

The supply/discharge plate 46 is formed in an annular shape when viewed from the axial direction. The outer diameter of the supply/discharge plate 46 is approximately equal to or slightly smaller than the diameter of the inner peripheral surface 7c of the first housing 7 . Therefore, the supply/discharge plate 46 is arranged at the first end portion 10b of the thick portion 10 so as to be fitted to the inner peripheral surface 7c of the first housing 7 .

A female screw portion 47 is formed on the outer peripheral portion of the supply/discharge plate 46 at a position corresponding to the first through hole 19 of the first housing 7 . The bolt 20 is inserted from the second housing 8 side into the second through hole 22 and the first through hole 19 of the first housing 7 in this order, and the bolt 20 is tightened to the female screw portion 47 of the supply/discharge plate 46 . As a result, the bolts 20 fasten the first housing 7, the second housing 8, and the supply/discharge plate 46 together to integrate them.

A plurality of through holes 46 a are formed in the supply/discharge plate 46 radially inward of the female threaded portion 47 so as to extend through the supply/discharge plate 46 in the thickness direction. Hydraulic oil is supplied to the working chambers 66a and 66b and discharged from the working chambers 66a and 66b through the through holes 46a (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 46a is thirteen. Each through-hole 46a is formed so that the opening on the thick portion 10 side is located in the center between the pin grooves 10a adjacent in the circumferential direction and radially inward of the inner peripheral surface 10d of the thick portion 10. It is

A plate-side labyrinth portion 48 is formed on most of the inner peripheral surface 46 b of the supply/discharge plate 46 excluding the end portion in the second direction. The plate-side labyrinth portion 48 is formed by making the inner diameter larger than the inner diameter of the inner peripheral surface 46b of the supply/discharge plate 46 via the stepped portion 48a. The plate-side labyrinth portion 48 cooperates with the rotating portion 3 to form a third labyrinth 49 . The third labyrinth 49 prevents hydraulic oil from leaking from between the supply/discharge plate 46 and the rotating portion 3 (details will be described later).

<Rotating part>
The rotating portion 3 rotatably held in the housing portion 2 includes a carrier portion 6 rotatably supported on both sides in the axial direction via respective bearings 12 and 13, and a plurality of ( For example, in this embodiment, three crankshafts 4 and oscillating gears 5 rotatably supported by the crankshafts 4 are main components.
The carrier part 6 is divided in the axial direction and consists of a first carrier 31 arranged on the first direction side and a second carrier 32 arranged on the second direction side.

The first carrier 31 includes a disk-shaped substrate portion 33 and a plurality of (for example, three in the present embodiment) projecting in the second direction from a second end portion 33b on the second direction side of the substrate portion 33. The strut portion 34 is integrally molded.
An outer peripheral surface 33c of the substrate portion 33 is formed such that its outer diameter gradually increases from the second end portion 33b toward the first end portion 33a on the first direction side via a stepped portion.

That is, the outer peripheral surface 33c of the substrate portion 33 has a first outer peripheral surface 33d and a large step portion 33h at the first direction side end of the first outer peripheral surface 33d from the second end portion 33b side. a second outer peripheral surface 33e formed; a third outer peripheral surface 33f having a large outer diameter formed via a small stepped portion 33i at the end of the second outer peripheral surface 33e in the first direction; and a fourth outer peripheral surface 33g formed to have a large outer diameter through a middle stepped portion 33j at the one-direction side end.

A portion corresponding to the first outer peripheral surface 33 d of the first carrier 31 is inserted into the plate-side labyrinth portion 48 of the supply/discharge plate 46 . The outer diameter of the first outer peripheral surface 33 d is slightly smaller than the inner diameter of the plate-side labyrinth portion 48 . The second end portion 33b of the first carrier 31 is located slightly forward of the stepped portion 48a of the supply/discharge plate 46. As shown in FIG. Thus, the first outer peripheral surface 33 d of the first carrier 31 , the second end portion 33 b , and the plate-side labyrinth portion 48 of the supply/discharge plate 46 constitute the third labyrinth 49 .

The inner race 12b of the first bearing 12 is fitted to the third outer peripheral surface 33f. Positioning between the first bearing 12 and the first carrier 31 is performed by the inner race 12b coming into contact with the intermediate stepped portion 33j. Thereby, positioning of the first carrier 31 with respect to the first housing 7 is performed. A first carrier 31 is rotatably supported by the first housing 7 via a first bearing 12 .

A fourth outer peripheral surface 33g of the first carrier 31 faces the seal accommodating portion 14 of the first housing 7 in the radial direction. That is, the seal portion 15 is arranged between the fourth outer peripheral surface 33 g of the first carrier 31 and the seal accommodating portion 14 of the first housing 7 .

A disk portion 35 having a circular shape when viewed from the axial direction is integrally formed with the first direction side end of the fourth outer peripheral surface 33g. A second end 35b of the disc portion 35 on the second direction side faces the first end 7b of the first housing 7 in the axial direction. The outer diameter of the disc portion 35 is the same as the diameter of the outer peripheral surface 7 a of the first housing 7 . A second end portion 35b of the disk portion 35 has an annular seal housing recess portion 36 formed in the outer peripheral portion thereof when viewed from the axial direction. The seal housing recess 36 is smoothly connected to the fourth outer peripheral surface 33g. A portion of the seal portion 15 is also accommodated in the seal accommodation recess 36 . As a result, the space between the first housing 7 and the first carrier 31 (rotating portion 3) is sealed.

A first carrier-side second labyrinth portion 37 having a small outer diameter is formed on the outer peripheral edge of the second end portion 35b of the disk portion 35 via a step. The first carrier-side second labyrinth portion 37 and the first carrier-side first labyrinth portion 16 formed in the first housing 7 constitute a first labyrinth 38 . Since the first labyrinth 38 is arranged on the radially outer side of the seal portion 15, it is possible to reliably prevent dust and the like from entering from the outside through the gap between the first housing 7 and the first carrier 31 (rotating portion 3). .

An outer flange portion 39 projecting radially outward is formed on the outer peripheral surface 35c of the disc portion 35 . The outer flange portion 39 is for attaching the hydraulic motor 1 to an external device (not shown). The outer flange portion 39 is formed with through holes 39a through which bolts (not shown) pass through in the thickness direction (axial direction) of the outer flange portion 39 .

In the second end portion 33b of the substrate portion 33, a plurality of (for example, three in this embodiment) shaft support recesses 44 are formed in the circumferential direction near the outer peripheral portion (slightly radially inward of the first outer peripheral surface 33d). formed at intervals. 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, it is not limited to this, and various bearings such as ball bearings can be used.

A plurality of supply passages 41, a plurality of discharge passages 42, and a tank passage 43 are formed in the substrate portion 33 radially inward of the second outer peripheral surface 33e over the entire axial direction of the substrate portion 33. there is
The supply path 41 is a flow path to which hydraulic oil is supplied from a hydraulic pump (not shown). A second direction side end of the supply path 41 is opened via a large stepped portion 33h. That is, each supply path 41 has a supply opening 41a in the large stepped portion 33h.
The discharge path 42 is a flow path through which hydraulic oil in the hydraulic motor 1 is discharged. The second direction side end of the discharge path 42 is also opened via the large stepped portion 33h. That is, each discharge path 42 has a discharge opening 42a in the large stepped portion 33h.

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 first housing 7, respectively. For example, in the present embodiment, the number of supply paths 41 and the number of discharge paths 42 are one less than the number of through-holes 46a of the supply/discharge plate 46, ie, 12 each.
The supply openings 41a of the supply path 41 and the discharge openings 42a of the discharge path 42 are arranged alternately in the circumferential direction on the same pitch circle. Each of the supply openings 41a and each of the discharge openings 42a forms a pair and is arranged at regular intervals in the circumferential direction.

The tank passage 43 is a passage for returning hydraulic oil that has leaked from the hydraulic motor 1 back to a tank (not shown). A second direction side end of the tank passage 43 communicates with a bottom portion 44 a of the shaft support recess 44 .

The first direction side ends of the supply path 41 , the discharge path 42 , and the tank path 43 communicate with an oil distribution portion 45 provided at the first end portion 33 a of the substrate portion 33 on the first direction side. The oil distributor 45 has a plurality of distribution channels (not shown). Hydraulic oil from the hydraulic pump is supplied to the supply passage 41 via these distribution passages. In addition, the hydraulic oil discharged to the discharge passage 42 is returned to the tank through the distribution passage and is returned to the supply passage 41 again. The hydraulic oil discharged to the tank passage 43 is also returned to the tank through the distribution passage. In addition, the detail about the effect|action of hydraulic oil is mentioned later.

A gap is formed between the large step portion 33 h of the first carrier 31 and the supply/discharge plate 46 . A sliding plate 50 is arranged in this gap. The sliding plate 50 is formed in an annular shape when viewed from the axial direction. The sliding plate 50 has an inner peripheral surface fitted to the first outer peripheral surface 33 d of the first carrier 31 , and is provided so as to be non-rotatable and axially slidable relative to the first carrier 31 . The thickness of the sliding plate 50 is smaller than the gap between the large stepped portion 33h and the supply/discharge plate 46 .

A plurality of through holes 50c are formed in the slide plate 50 so as to correspond to the supply opening 41a of the supply passage 41 and the discharge opening 42a of the discharge passage 42. As shown in FIG. A through hole 50c corresponding to the supply opening 41a is arranged coaxially with the supply opening 41a. A through hole 50c corresponding to the discharge opening 42a is arranged coaxially with 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 in the supply path 41 and the discharge path 42 . The piston 51 is biased toward the slide plate 50 by springs (not shown) provided in the supply passage 41 and the discharge passage 42 . The piston 51 is therefore pressed against the sliding plate 50 .

The thickness of the sliding plate 50 is smaller than the gap between the large stepped portion 33h and the supply/discharge plate 46 . Therefore, the piston 51 protrudes from the large stepped portion 33h and abuts against the slide plate 50 due to the spring. As a result, the sliding plate 50 is pressed against the supply/discharge plate 46 . Thereby, each supply path 41 and the through hole 50 c of the slide plate 50 are communicated via the piston 51 . Further, each discharge passage 42 and the through hole 50c of the sliding plate 50 communicate with each other through the piston 51. As shown in FIG. Furthermore, each through-hole 50c of the slide plate 50 and the through-hole 46a of the supply/discharge plate 46 communicate with each other.

The pillar portion 34 of the first carrier 31 has a triangular columnar shape when viewed from the axial direction. Each support column 34 is arranged so as to be positioned between the shaft support recesses 44 of the substrate portion 33 in the circumferential direction. That is, the support columns 34 are arranged on the second end portion 33b of the substrate portion 33 at regular intervals in the circumferential direction. The pitch circle diameter of each strut portion 34 and the pitch circle diameter of the shaft support recess 44 are substantially the same.

A tip portion 34a of the support portion 34 is formed flat. A tip portion 34 a of the strut portion 34 is positioned on the same plane as the second end portion 7 d of the first housing 7 . A female threaded portion 52 for a reamer bolt is formed at the tip portion 34 a of the support portion 34 .

The reamer bolt female threaded portion 52 includes a fitting recess 52a formed along the axial direction from the tip 34a of the support 34 to the center of the support 34 in the axial direction, and a fitting recess 52a extending from the bottom of the fitting recess 52a in the first direction. and a female threaded portion body 52b extending toward. The first carrier 31 and the second carrier 32 are integrated by tightening a reamer bolt (an example of another fixing portion in the claims) 53 to the female threaded portion 52 for reamer bolt.

The second carrier 32 is formed in a disc shape. The second carrier 32 is arranged and positioned such that the first end 32 a on the first direction side abuts against the tip 34 a of the support 34 that constitutes the first carrier 31 . Therefore, a gap that is the same as the height of the column portion 34 is formed between the substrate portion 33 of the first carrier 31 and the second carrier 32 . By surrounding this gap with the thick portion 10 of the first housing 7, an oscillating gear housing portion 60 for housing the oscillating gear 5 is formed.

A first end portion 32a of the second carrier 32 is formed flat throughout. A fitting hole 54 is formed through the second carrier 32 in the thickness direction at a position corresponding to the female threaded portion 52 for the reamer bolt. A reamer bolt 53 is inserted into the fitting hole 54 from the second direction side of the second carrier 32, and this reamer bolt 53 is tightened to the female threaded portion main body 52b via the fitting recess 52a of the support 34, whereby the first carrier is 31 and the second carrier 32 are integrated.

The reamer bolt 53 includes a shaft portion 53a, a male threaded portion 53b projecting from the first direction side end of the shaft portion 53a and formed coaxially with the shaft portion 53a, and a shaft portion 53a at the second direction side end of the shaft portion 53a. and a coaxially formed head 53c. When the reamer bolt 53 is tightened to the reamer bolt female threaded portion 52 , the shaft portion 53 a of the reamer bolt 53 is fitted into the fitting recess 52 a of the post portion 34 and the fitting hole 54 of the second carrier 32 . That is, the shaft portion 53 a of the reamer bolt 53 is arranged across 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 32b of the second carrier 32 on the second direction side. A head portion 53 c of the reamer bolt 53 is inserted into the counterbore portion 55 . As a result, the projection height of the head 53c of the reamer bolt 53 from the second end 32b of the second carrier 32 is suppressed.

The outer peripheral surface 32c of the second carrier 32 has a reduced-diameter portion 56 with a small outer diameter formed via a stepped portion 56a in the major portion of the center in the axial direction. The inner race 13b of the second bearing 13 is fitted to the reduced diameter portion 56. As shown in FIG. Thereby, 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 first direction side of 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 57a. The outer diameter of the second carrier side second labyrinth portion 57 is slightly smaller than the inner diameter of the second carrier side first labyrinth portion 25 of the second housing 8 .

The tip of the second carrier-side second labyrinth portion 57 is positioned slightly before the stepped portion 25 a of the second carrier-side first labyrinth portion 25 . Thus, the second labyrinth 40 is configured 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 58 are formed at regular intervals in the circumferential direction slightly radially inward of the second carrier-side second labyrinth portion 57 of the second carrier 32 . . The shaft support hole 58 rotatably supports the crankshaft 4 . These shaft support holes 58 and the corresponding shaft support recesses 44 of the first carrier 31 are positioned coaxially. A second bearing 59 b is fitted in the shaft support hole 58 . The second bearing 59b is, for example, a sliding bearing. However, it is not limited to this, and various bearings such as ball bearings can be used.

The crankshaft 4 is rotatably supported in the shaft support recess 44 and the shaft support hole 58 via bearings 59a and 59b. That is, in this embodiment, the number of crankshafts 4 is three. The crankshaft 4 includes bearing portions 4a and 4b (first bearing portion 4a and second bearing portion 4b) rotatably supported in the shaft support recess 44 and the shaft support hole 58 via bearings 59a and 59b; A cylindrical eccentric portion 4c provided between the portions 4a and 4b is integrally molded.

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 caused by thrust bearings 61a and 61b (first thrust bearing 61a and second thrust bearing 61b) provided axially outside the respective bearing portions 4a and 4b and the first carrier 31. A first collar 70a provided in the shaft support recess 44 and a second collar 70b provided in the shaft support hole 58 of the second carrier 32 are regulated. Of the two thrust bearings 61a and 61b, the second thrust bearing 61b provided in the shaft support hole 58 of the second carrier 32 is restricted from moving in the second direction by a retaining ring 62 provided in the shaft support hole 58. It is

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

The oscillating gear 5 is made of high steel, for example. The outer diameter of the oscillating gear 5 is smaller than the diameter of the inner peripheral surface 10 d of the thick portion 10 so that it can be stored in the oscillating gear storage portion 60 . The axial thickness of the oscillating gear 5 is the same as that of the eccentric portion 4c. Therefore, the position of the end of the oscillating gear 5 in the second direction and the position of the first end 8b of the second housing 8 are substantially on the same plane. A support hole 63 through which the eccentric portion 4c of the crankshaft 4 passes is formed in the oscillating gear 5 at a position corresponding to the crankshaft 4 .

Each support hole 63 is arranged at regular intervals in the circumferential direction. The support holes 63 are provided with third bearings 59c. Axial movement of the oscillating gear 5 with respect to the crankshaft 4 is restricted by retaining rings 67 provided at both ends of the third bearing 59c in the axial direction. With such a configuration, the crankshaft 4 restricts the rotation of the oscillating gear 5 to oscillating rotation.

Further, the oscillating gear 5 is formed with a relief hole 64 at a position corresponding to the support pillar 34 of the first carrier 31 , through which the support pillar 34 is passed. The shape of the relief hole 64 seen from the axial direction is triangular so as to correspond to the shape of the support 34 seen from the axial direction. The size of the relief hole 64 is formed sufficiently larger than the outer surface shape of the support pillar 34 so that each support 34 does not interfere with the oscillating and rotating motion of the oscillating gear 5 .

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

The oscillating gear 5 is always in contact with the internal pin 90 at any point from the tip 65a to the bottom 65b during the oscillating rotation. As a result, two working chambers 66a and 66b (first working chamber 66a, A second working chamber 66b) is formed. The two working chambers 66a and 66b are formed symmetrically with respect to the axial direction.

A plurality of through holes 46a of the supply/discharge plate 46 communicate with these working chambers 66a and 66b. Hydraulic oil is supplied to the working chambers 66a and 66b and discharged from the working chambers 66a and 66b through the through holes 46a. As a result, the hydraulic motor 1 is rotationally driven. The operation of the hydraulic motor 1 will be described in detail below.

<Operation of hydraulic motor>
Next, operation of the hydraulic motor 1 will be described.
Hydraulic oil supplied from a hydraulic pump (not shown) is supplied to the hydraulic motor 1 via an oil distribution section 45 to each supply passage 41 . Hydraulic oil supplied to each supply path 41 is supplied to the working chambers 66a and 66b via the through hole 50c of the slide plate 50 and the through hole 46a of the supply/discharge plate 46. As shown in FIG.

Here, the number of supply paths 41 (the supply opening 41a and the through holes 50c of the sliding plate 50 communicating with the supply opening 41a) is one less than the number of through holes 46a of the supply/discharge plate 46. As shown in FIG. Also, the number of discharge passages 42 (the discharge openings 42a and the through holes 50c of the sliding plate 50 leading to the discharge openings 42a) is one less than the number of through holes 46a of the supply/discharge plate 46. As shown in FIG. Therefore, one of the two working chambers 66a and 66b is connected only to the supply path 41 via the through hole 46a of the supply/discharge plate 46. As shown in FIG. Further, only the discharge path 42 communicates with the other of the two working chambers 66a and 66b through the through hole 46a of the supply/discharge plate 46. As shown in FIG.

Then, the pressure inside one of the two working chambers 66a and 66b becomes higher than the pressure inside the other one of the two working chambers 66a and 66b. In order to make the explanation easier to understand, the case where the pressure in the working chamber 66a (left side in FIG. 2) is higher than the pressure in the working chamber 66b (right side in FIG. 2) out of the two working chambers 66a and 66b will be described below. explain. Further, in the following description, the high-pressure working chamber 66a will be referred to as the 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. A high pressure working chamber 66 a communicates with the supply passage 41 . A low-pressure working chamber 66 b communicates with the discharge passage 42 .

By supplying hydraulic fluid to the high-pressure working chamber 66a, the oscillating gear 5 is pressed toward the low-pressure working chamber 66b (see arrow Y1 in FIG. 2). Hydraulic oil in the low-pressure working chamber 66b is discharged through the discharge passage 42. As shown in FIG. As a result, the internal pin 90 and the external teeth 65 of the oscillating gear 5 are meshed on the low-pressure working chamber 66b side. Then, since the number of teeth of the external tooth 65 is one less than the number of teeth of the internal tooth pin 90, the oscillating gear 5 is slightly displaced in the rotational direction.

At this time, the carrier portion 6 is shifted in the rotational direction by being taken by the oscillating gear 5 via the crankshaft 4 . That is, the rotating part 3 is slightly rotated with respect to the housing part 2 . Then, the slide plate 50 is rotated with respect to the supply/discharge plate 46 . Then, 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. As the oscillating gear 5 is oscillatingly rotated, the high pressure working chamber 66a is also slightly displaced in the rotational direction of the low pressure working chamber 66b.

When the through hole 50c of the slide plate 50 and the through hole 46a of the supply/discharge plate 46 communicate with each other, the hydraulic oil is supplied to the high pressure working chamber 66a again. Also, hydraulic fluid is discharged from the low-pressure working chamber 66b. By sequentially repeating this, the rotating portion 3 is rotated with respect to the housing portion 2 . Output is obtained by this rotation.

In this way, the hydraulic motor 1 is able to prevent the number of the supply paths 41 (the supply openings 41a and the through holes 50c of the sliding plate 50 leading to the supply openings 41a) from mismatching with the number of the through holes 46a of the supply/discharge plate 46, And by utilizing the mismatch between the number of discharge passages 42 (discharge openings 42a and through holes 50c of the slide plate 50 leading to the discharge openings 42a) and the number of through holes 46a of the supply/discharge plate 46, the sliding plate The communication state between the through hole 50c of the plate 50 and the through hole 46a of the supply/discharge plate 46 is sequentially switched in the circumferential direction. As a result, hydraulic oil is selectively supplied to and discharged from the through holes 46a of the supply/discharge plate 46 to the working chambers 66a and 66b, and the rotating portion 3 is rotated.

The carrier section 6 forming the rotating section 3 is divided into a first carrier 31 and a second carrier 32 . Since the first carrier 31 and the second carrier 32 are fixed by the reamer bolt 53 , power transmission between the first carrier 31 and the second carrier 32 is performed via the reamer bolt 53 . A shaft portion 53 a of the reamer bolt 53 is arranged across the first carrier 31 and the second carrier 32 . Therefore, power transmission between the first carrier 31 and the second carrier 32 is performed more efficiently than when the male threaded portion 53b straddles the first carrier 31 and the second carrier 32 .

Hydraulic oil supplied to the working chambers 66a and 66b leaks into the minute gaps between the carriers 31 and 32 and the crankshaft 4 through the minute gaps between the crankshaft 4 and the oscillating gear 5. put out. The leaked hydraulic oil is discharged to the tank passage 43 through the shaft support recess 44 formed in the first carrier 31 . The hydraulic oil discharged to the tank passage 43 is returned to a tank (not shown).

Here, on the first direction side of the oscillating gear 5, a third labyrinth 49 is formed by the first outer peripheral surface 33d of the first carrier 31, the second end portion 33b, and the plate-side labyrinth portion 48 of the supply/discharge plate 46. It is configured. A second labyrinth 40 is formed on the second direction side of the oscillating gear 5 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. It is Therefore, the hydraulic oil leaking from the working chambers 66a and 66b through the minute gap between the crankshaft 4 and the oscillating gear 5 flows between the first housing 7 and the first carrier 31 and the second housing 8. and the second carrier 32.

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

<How to assemble the hydraulic motor>
Next, a method for assembling the hydraulic motor 1 will be described with reference to FIG.
FIG. 5 is an explanatory view for explaining a method of assembling the hydraulic motor 1, and is an exploded view of FIG.
As shown in FIG. 5, before assembling the hydraulic motor 1, the crankshaft 4 is assembled to the oscillating gear 5 in advance. Also, the piston 51 and the sliding plate 50 are assembled in advance to the first carrier 31 .

First, the first bearing 12 is assembled to either the first bearing housing portion 11 of the first housing 7 or the third outer peripheral surface 33f of the first carrier 31 (first bearing assembly step). 5 shows a state in which the first bearing 12 is pre-assembled in the first bearing accommodating portion 11 of the first housing 7 for convenience of illustration.
Also, the second bearing 13 is assembled to either the second bearing housing portion 24 of the second housing 8 or the reduced diameter portion 56 of the second carrier 32 (second bearing assembly step). 5 shows a state in which the second bearing 13 is pre-assembled in the second bearing accommodating portion 24 of the second housing 8 for convenience of illustration.

Subsequently, the rotating portion 3 is assembled to the first housing 7 and the second housing 8 via the bearings 12 and 13 (rotating portion attaching step).
At this time, the first carrier 31 and the second carrier 32 are assembled from both axial sides of the crankshaft 4 . After that, the first carrier 31 and the second carrier 32 are fixed by the reamer bolt 53 (arrow Y2 in FIG. 5).

Also, in the rotating part assembling process, the seal part 15 is assembled to the seal accommodating part 14 of the first housing 7 and the seal accommodating concave part 36 of the first carrier 31 . Further, the supply/discharge plate 46 is arranged on the first end portion 10b of the thick portion 10 that is formed in the first housing 7 in advance. Then, the dividing surface of the housing portion 2, that is, the second end portion 7d of the first housing 7 and the first end portion 8b of the second housing 8 are overlapped.

Subsequently, a preload is applied to the first bearing 12 and the second bearing 13 (preload step).
A preload is an axial load applied in advance to a bearing in order to improve the rotational accuracy and durability of the bearing. In this embodiment, for example, the first housing 7 and the second housing 8 are collectively lightly pressed to the right in FIG. 5 (see arrow Y3 in FIG. 5). Thereby, a preload is applied to the first bearing 12 and the second bearing 13 . Then, the manufacturing errors of the first bearing housing portion 11 of the first housing 7, the second bearing housing portion 24 of the second housing 8, the third outer peripheral surface 33f of the first carrier 31, and the reduced diameter portion 56 of the second carrier 32 As a result, the first housing 7 and the second housing 8 move slightly relative to each other in the radial direction.

As a result, the first bearing housing portion 11 of the first housing 7, the second bearing housing portion 24 of the second housing 8, the third outer peripheral surface 33f of the first carrier 31, and the reduced diameter portion 56 of the second carrier 32 are manufactured. Errors are absorbed. In other words, position adjustment (centering) between the first housing 7 (first bearing 12) and the second housing 8 (second bearing 13) is completed.

At this time, since the second end portion 7d of the first housing 7 and the first end portion 8b of the second housing 8 are formed flat as a whole, the diameters of the first housing 7 and the second housing 8 This relative movement occurs smoothly without being constrained by the amount of relative movement in direction. That is, for example, if a step is formed at the second end 7d of the first housing 7 and the first end 8b of the second housing 8, this step causes the first housing 7 and the second housing 8 to move in the radial direction. relative movement is inhibited. In the present embodiment, relative movement in the radial direction between the first housing 7 and the second housing 8 is smoothly performed without such hindrance.

Subsequently, the bolt 20 is inserted from the second housing 8 side into the second through hole 22 and the first through hole 19 of the first housing 7 in this order. Further, the bolt 20 is tightened to the female screw portion 47 of the supply/discharge plate 46 (see arrow Y4 in FIG. 5). As a result, the first housing 7, the second housing 8 and the supply/discharge plate 46 are fastened together and integrated (housing fixing step).
After that, the cover 29 is fixed to the second housing 8 with the bolts 30 (see arrow Y5 in FIG. 5). Thus, assembly of the hydraulic motor 1 is completed.

The bolts 20 for fixing the first housing 7 and the second housing 8 are desirably pre-tightened temporarily. It is desirable to retighten the bolt 20 after temporary tightening. Temporary tightening means tightening the bolts 20 to such an extent that the first housing 7 and the second housing 8 can move relative to each other by applying a certain amount of load to the first housing 7 and the second housing 8 . Retightening refers to completely tightening the bolt 20 with a torque required to integrate (perfectly fix) the first housing 7 and the second housing 8 .

By performing the temporary tightening, it is possible to prevent the housings 7 and 8 from rattling during the preloading process. Therefore, position adjustment (centering) between the first housing 7 (first bearing 12) and the second housing 8 (second bearing 13) can be easily performed. In addition, it is possible to prevent the relative positions of the first housing 7 and the second housing 8 from unintentionally shifting after the preloading process. After that, by performing additional tightening, the first housing 7 and the second housing 8 can be easily positioned, and the first housing 7 and the second housing 8 can be attached while maintaining the positional accuracy obtained by this positioning. It can be fixed securely.

As described above, in the above-described embodiment, the housing portion 2 is divided in the axial direction to be composed of the first housing 7 and the second housing 8 . Two bearings 12 and 13 for rotatably supporting the rotating portion 3 in the housing portion 2 are separately provided in each of the housings 7 and 8 . In other words, the first bearing 12 and the second bearing 13 are arranged on both sides of the second end 7d of the first housing 7 and the first end 8b of the second housing 8, which are the dividing surfaces of the housing portion 2. are provided. Therefore, by adjusting the positions of the first housing 7 and the second housing 8, the two bearings 12 and 13 can be adjusted (centered). That is, there is no need to apply high-precision processing such as simultaneous processing to each portion where the two bearings 12 and 13 of the housing portion 2 are fitted. As a result, assembly of the hydraulic motor 1 can be facilitated.

Further, the hydraulic motor 1 uses a plurality of bolts 20 as a fixing portion for fixing the first housing 7 and the second housing 8 in a state in which a preload is applied to the first bearing 12 and the second bearing 13. there is Therefore, the positions of the first housing 7 and the second housing 8 can be adjusted after the first housing 7 and the second housing 8 are temporarily tightened with the bolts 20 . Thereafter, by further tightening the bolts 20, the housings 7, 8 can be reliably fixed while preventing the housings 7, 8 from being displaced.
By temporarily fastening the first housing 7 and the second housing 8 together, it is possible to prevent the housings 7 and 8 from being unintentionally displaced when adjusting the positions of the housings 7 and 8 . As a result, the assembly of the hydraulic motor 1 can be made easier.

The second end portion 7d of the first housing 7 and the first end portion 8b of the second housing 8, which are the dividing surfaces of the housing portion 2, are formed flat as a whole. Therefore, relative movement between the first housing 7 and the second housing 8 can be performed smoothly. Therefore, assembly of the hydraulic motor 1 can be further facilitated.

The dividing surface of the housing portion 2, that is, the position of the first end portion 8b of the second housing 8 and the position of the end portion of the eccentric portion 4c of the crankshaft 4 in the second direction are substantially on the same plane. Also, the position of the first end 8b of the second housing 8 and the position of the end of the rocking gear 5 in the second direction are substantially on the same plane. In this way, since each part is located on substantially the same plane, the ends 7d and 8b can be easily overlapped even if the inside of each housing 7 and 8 is difficult to see.

The hydraulic motor 1 has an internal pin 90 provided on the first housing 7 . The rotating portion 3 includes a carrier portion 6, a crankshaft 4 rotatably supported by the carrier portion 6, and an oscillating gear 5 which is oscillatingly rotated by the crankshaft 4 and meshed with an internal pin 90. . With this configuration, hydraulic oil is supplied to and discharged from working chambers 66a and 66b formed between the inner peripheral surface 7c of the first housing 7 and the outer peripheral surface of the oscillating gear 5. , the hydraulic motor 1 can be rotationally driven. This rotational drive allows high rotational torque to be obtained. A divided housing portion 2 can be suitably used for such a hydraulic motor 1 .

The hydraulic motor 1 has a supply/discharge plate 46 for selectively supplying/discharging hydraulic oil to/from the working chambers 66a and 66b. The supply/discharge plate 46 is arranged at the first end portion 10b of the thick portion 10 (the first direction side end of the rocking gear 5). Such a supply/discharge plate 46 is fixed to the first housing 7 using bolts 20 . Since the supply/discharge plate 46 is also fixed using the bolts 20 for fixing the first housing 7 and the second housing 8, the number of parts of the hydraulic motor 1 can be reduced.

As a method of assembling the hydraulic motor 1, the first housing 7 and the second housing 8 are fixed (housing fixing process) through a first bearing assembling process, a second bearing assembling process, a rotating part assembling process, and a preloading process. . Therefore, the position adjustment (centering) between the first bearing 12 and the second bearing 13 can be easily performed, and the assembly of the hydraulic motor 1 can be facilitated.

In the rotating part assembling process, the first carrier 31 and the second carrier 32 are fixed by the reamer bolts 53 . After that, the bolts 20 are used to fix the first housing 7 and the second housing 8 together. Therefore, position adjustment (centering) of the housings 7 and 8 (bearings 12 and 13) can be easily performed regardless of the configuration of the rotating portion 3 .

A reamer bolt 53 is used to assemble the first carrier 31 and the second carrier 32 . A shaft portion 53 a of the reamer bolt 53 is arranged across the first carrier 31 and the second carrier 32 . Therefore, power transmission between the first carrier 31 and the second carrier 32 can be efficiently performed as compared with the case where the male screw portion 53b straddles the first carrier 31 and the second carrier 32 .

It should be noted that the present invention is not limited to the above-described embodiments, and includes various modifications of the above-described embodiments within the scope of the present invention.
For example, in the above embodiments, the hydraulic motor 1 was described as the rotary device. However, it is not limited to this, and the hydraulic motor 1 can also be used as a hydraulic pump. In this case, the oscillating gear 5 is oscillatingly rotated by rotating the crankshaft 4 . As a result, the volumes of the working chambers 66a and 66b are changed, and hydraulic oil can be discharged through the supply passage 41 or the discharge passage 42. As shown in FIG.

Moreover, the above configuration can be applied to various rotating devices having a housing portion that rotatably supports a rotating portion. For example, the above configuration can be applied to a rotary device having a gear rotatably supported by a housing.
Although the case where hydraulic oil is used as the fluid has been described, various fluids other than hydraulic oil can be used. For example, water can be used instead of hydraulic oil. The fluid is not limited to liquid, and may be gas or the like.

In the above-described embodiment, the bolt 20 is used as the fixing portion for fixing the first housing 7 and the second housing 8 together. The case where the reamer bolt 53 is used as the fixing portion for fixing the first carrier 31 and the second carrier 32 has been described. However, the present invention is not limited to this, as long as the housings 7 and 8 can be fixed or the carriers 31 and 32 can be fixed in place of the bolts 20 and reamer bolts 53 . For example, a rivet or the like may be used as each fixing portion.

In the above-described embodiment, the second end portion 7d of the first housing 7 and the first end portion 8b of the second housing 8 are formed flat as a whole. However, it is not limited to this, and each of the ends 7d and 8b may have some steps. The first housing 7 (first bearing 12) and the second housing 8 (second bearing 13) should be able to move relative to each other to the extent that the positions of the first housing 7 (first bearing 12) and the second housing 8 (second bearing 13) can be adjusted during the preloading process. .

For example, one of a portion of the second end 7d of the first housing 7 and a first end 8b of the second housing 8 corresponding to the second end 7d is provided with a recess, and the other is provided with a recess. A protrusion to be fitted may be provided. These concave portions and convex portions may be formed over the entire circumference and fitted together, or may be formed only in a part of the entire circumference. In the case of forming a concave portion or a convex portion only on a portion of the entire circumference, for example, a portion of the second end portion 7d of the first housing 7 and a first portion of the second housing 8 corresponding to the second end portion 7d. A pin may be provided on one of the end portions 8b, and a concave portion for fitting the pin may be provided on the other end portion 8b. The pins and protrusions may be formed integrally with the respective housings 7 and 8, or may be formed separately.

In these cases, the size of the protrusion should be set to the extent that the positions of the housings 7 and 8 (bearings 12 and 13) can be adjusted relative to the size of the recess.
That is, for example, when forming recesses and protrusions over the entire circumference and fitting them together, the recesses and protrusions are often formed based on the fitting tolerances of the JIS standard. However, in the present embodiment, since the positions of the housings 7 and 8 (bearings 12 and 13) are adjusted, the processing accuracy of the fitting tolerance of the JIS standard is not required. For this reason, the processing cost can be reduced even when concave portions and convex portions are formed in the respective housings 7 and 8 .

In addition, by providing the concave portion and the convex portion, when the second end portion 7d of the first housing 7 and the first end portion 8b of the second housing 8 are overlapped, the first housing 7 and the second housing 8 are separated from each other. Relative positions can be determined approximately. After provisionally positioning the housings 7 and 8 in this way, the final position adjustment (centering) of the housings 7 and 8 (the bearings 12 and 13) can be performed. Therefore, the workability of assembling the housings 7 and 8 can be improved.

In the above-described embodiment, the positions of the second end portion 7d of the first housing 7 and the first end portion 8b of the second housing 8, which are the dividing surfaces of the housing portion 2, and the second direction of the eccentric portion 4c of the crankshaft 4 The position of the end portion of the has been described as being substantially on the same plane. However, it is not limited to this, and the dividing surface of the housing part 2 can be determined arbitrarily. The bearings 12 and 13 may be separately provided on both sides of the dividing surface, that is, on each of the housings 7 and 8 .

In the above-described embodiment, the first housing 7 is provided with a plurality of internal teeth pins 90 , and these internal teeth pins 90 are internal teeth meshing with the external teeth 65 of the oscillating gear 5 . However, it is not limited to this, and internal teeth may be formed directly on the inner peripheral surface 7c of the first housing 7 (the inner peripheral surface 10d of the thick portion 10).

In the above-described embodiment, the case where the supply/discharge plate 46 is fixed to the first housing 7 using the bolts 20 has been described. However, the fixing member other than the bolt 20 may be used to fix the supply/discharge plate 46 to the first housing 7 without being limited thereto. Also, the supply/discharge plate 46 does not have to be fastened together with the first housing 7 and the second housing 8 .
In this case, the housings 7 and 8 may be integrated by providing, for example, an outer flange portion for housing fixation on the outer peripheral surface of each of the housings 7 and 8 and fixing the outer flange portion with bolts.

In the above embodiment, the case where the rotating part 3 has three crankshafts 4 and these crankshafts 4 restrict the swing gear 5 from swinging rotation has been described. However, it is not limited to this, and the rotating part 3 may have at least one crankshaft 4 . In this case, the crankshaft 4 becomes a so-called center crankshaft in which the second axis C2 of the crankshaft 4 and the first axis C1 of the rotating portion 3 are aligned. The rotation of the oscillating gear 5 is restricted by this center crankshaft.

In the above-described embodiment, the case where the first housing 7 and the second housing 8 are fixed by using, for example, eight bolts 20 has been described. However, the number of bolts 20 is not limited to this, and the number of bolts 20 can be arbitrarily determined according to the required fixing strength between the first housing 7 and the second housing 8 .
In the above-described embodiment, the case where the bearings 12 and 13 are provided in each of the first housing 7 and the second housing 8 in order to rotatably support the rotating portion 3 in the housing portion 2 has been described. However, the present invention is not limited to this, and each housing 7, 8 may be provided with one or more bearings.

Among the embodiments disclosed in this specification, those composed of a plurality of objects may be integrated, and conversely, those composed of a single object may be divided into a plurality of objects. be able to. Regardless of whether they are integrated or not, it is sufficient that they are constructed so as to achieve the object of the invention.

DESCRIPTION OF SYMBOLS 1... Hydraulic motor (rotating apparatus), 2... Housing part, 3... Rotating part, 4... Crankshaft, 5... Oscillating gear, 7... First housing, 7d... Second end (parting surface), 8... Second 2 housing, 8b... first end portion (dividing surface), 10... thick portion, 10d... inner peripheral surface, 12... first bearing (bearing), 13... second bearing (bearing), 20... bolt (fixing part , screw), 31... First carrier, 32... Second carrier (carrier), 46... Supply/discharge plate, 65... External tooth, 90... Internal tooth pin

Claims (8)

a housing portion consisting of a first housing and a second housing divided in the axial direction;
bearings respectively provided in the first housing and the second housing;
a rotating portion supported rotatably around the axis by the housing portion via each of the bearings;
a fixing portion that fixes the first housing and the second housing in a state in which preload is applied to each of the bearings;
rotating equipment. 2. The rotating device according to claim 1, wherein the fixing portion is a screw. 3. The rotating device according to claim 1, wherein the entire dividing surface of the housing portion is flat. having internal teeth provided on the inner peripheral surface of the housing portion,
The rotating part is
a carrier rotatably supported by the housing via the bearing;
a crankshaft rotatably supported by the carrier about another axis parallel to the axis;
an oscillating gear that is regulated to oscillating rotation by the crankshaft and is meshed with the internal teeth;
The rotating device according to any one of claims 1 to 3, comprising: a supply/discharge plate for supplying hydraulic fluid between the inner peripheral surface of the housing portion and the oscillating gear and for discharging hydraulic fluid from between the inner peripheral surface of the housing portion and the oscillating gear;
5. The rotating device according to claim 4, wherein the supply/discharge plate is arranged at one end of the oscillating gear in the axial direction, and is fixed to the housing portion by the fixing portion. a housing portion consisting of a first housing and a second housing divided in the axial direction and each having a flat dividing surface;
internal teeth provided on the inner peripheral surface of the first housing;
bearings respectively provided in the first housing and the second housing;
a carrier rotatably supported by the housing portion around the axis through each of the bearings;
a crankshaft rotatably supported by the carrier about another axis parallel to the axis;
an oscillating gear that is regulated to oscillating rotation by the crankshaft and is meshed with the internal teeth;
screws for fixing the first housing and the second housing in a state in which preload is applied to each of the bearings;
a supply and discharge plate for supplying hydraulic fluid between the inner peripheral surface of the first housing and the oscillating gear and for discharging hydraulic fluid from between the inner peripheral surface of the first housing and the oscillating gear;
with
The rotating device, wherein the supply/discharge plate is disposed at the first housing side end of the oscillating gear in the axial direction, and is fixed to the first housing by the screw. a housing portion consisting of a first housing and a second housing divided in the axial direction;
a first bearing provided in the first housing;
a second bearing provided in the second housing;
a rotating portion supported rotatably around the axis by the housing portion via the first bearing and the second bearing;
a fixing portion that fixes the first housing and the second housing;
A method for assembling a rotating device comprising:
a first bearing assembling step of assembling the first bearing to either the first housing or the rotating portion;
a second bearing assembling step of assembling the second bearing to either the second housing or the rotating portion;
a rotating portion assembling step of assembling the rotating portion to the first housing and the second housing via the first bearing and the second bearing after the first bearing assembling step and the second bearing assembling step;
a preloading step of applying a preload to the first bearing and the second bearing after the rotating portion assembling step;
a housing fixing step of fixing the first housing and the second housing by the fixing portion after the preloading step;
A method for assembling a rotating device having The rotating part is
a first carrier rotatably supported by the first housing via the first bearing;
a second carrier rotatably supported by the second housing via the second bearing;
has
8. The method for assembling a rotating device according to claim 7, wherein in the rotating portion assembling step, the first carrier and the second carrier are fixed by another fixing portion.

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