Rotating device

Abstract

The invention provides a rotating device. A reduction gear (1) according to one embodiment of the present invention is provided with: a housing (2); a first main bearing (41) and a second main bearing (42) disposed on both sides of the housing (2) in the axial direction; and a carrier (3) that is rotatably supported by the housing (2) via main bearings (41, 42). The carrier (3) has a substrate-side lubricant inflow hole (63) and an end-plate-side lubricant inflow hole (64) that communicate with the outside and a housing section (65) formed between the carrier (3) and the housing (2). The minimum opening widths (Ds, De) of the lubricant inflow holes (63, 64) are larger than the width between the outer ring (43) and the retainer (50) and the width between the inner ring (44) and the retainer (50) of the main bearings (41, 42).

Description

TECHNICAL FIELD

[0001] The present application relates to a rotary device. BACKGROUND

[0002] Hitherto, as a rotary device, a so-called eccentric swing type reduction device is known. This rotary device is provided with an internal gear (housing member), two gear carriers supported to the internal gear in a rotatable manner by bearings, and arranged opposite to each other in the rotational axis direction, a crankshaft (shaft body) supported to the gear carriers in a rotatable manner, having an eccentric portion, and an external gear arranged between the gear carriers. The external gear is supported to the crankshaft in a rotatable manner, and meshes with the internal gear. In this way, the external gear and the bearings of the eccentric swing type reduction device are closely combined.

[0003] As the bearings supporting the internal gear and the gear carriers in a rotatable manner, rolling bearings are used. The rolling bearings are provided with an outer ring provided on the internal gear side, an inner ring provided on the gear carrier side, a plurality of rolling elements arranged between the outer ring and the inner ring, and a retainer retaining the rolling elements.

[0004] In such a reduction device, the inside of the gear carrier is sufficiently filled with a lubricant. Thereby, the sliding resistance of the external gear, the meshing resistance between the internal gear and the external gear can be reduced, and the driving efficiency of the rotary device can be improved. In order to fill the inside of the gear carrier with the lubricant, the lubricant is injected from a gap of the bearing or the like. The gap of the bearing refers to between the outer ring and the retainer and between the inner ring and the retainer.

[0005] Prior art documents

[0006] Patent documents

[0007] Patent Document 1: Japanese Patent Application Publication No. 2013-124730 SUMMARY

[0008] PROBLEMS TO BE SOLVED BY THE INVENTION

[0009] However, as in the above-described prior art, even if the lubricant is to be filled from the gap of the bearing, the gap of the bearing is narrow, it is difficult to actively inject the lubricant into the inside of the gear carrier. Therefore, there is a problem that the work of improving the driving efficiency of the rotary device is troublesome.

[0010] The present application provides a rotary device capable of easily improving the driving efficiency.

[0011] MEANS FOR SOLVING THE PROBLEMS

[0012] A rotation device of one aspect of the present application includes: a first rotation body that is cylindrical; a pair of rolling bearings that are provided on the first rotation body; a second rotation body that is disposed on an inner side in a radial direction of the first rotation body; and a mechanism portion that is disposed on an inner side in a radial direction of the second rotation body, the pair of rolling bearings are disposed on both sides in an axial direction of the first rotation body, the second rotation body is supported to the first rotation body in a manner that is rotatable about a rotation axis by the rolling bearings, the rotation device includes: a housing portion that is formed between the first rotation body and the second rotation body; and a hole portion that communicates with an outside of the second rotation body and the housing portion, the housing portion houses the mechanism portion, the hole portion is disposed on the second rotation body, the rolling bearing includes: an outer ring that is disposed on the first rotation body side; an inner ring that is disposed on the second rotation body side; a plurality of rolling elements that are disposed between the outer ring and the inner ring; and a retainer that is disposed between the outer ring and the inner ring, the retainer retains the plurality of rolling elements, and a minimum opening width in an opening width of the hole portion that is orthogonal to a direction in which the hole portion extends is larger than a width between the outer ring and the retainer and a width between the inner ring and the retainer.

[0013] With this configuration, it is possible to easily inject, for example, a lubricant from the outside of the second rotation body to the housing portion inside the second rotation body via the hole portion. Also, the maximum opening width of the hole portion is larger than the width between the outer ring and the retainer and the width between the inner ring and the retainer. Therefore, compared to between the outer ring and the retainer and between the inner ring and the retainer, it is possible to more positively inject the lubricant from the hole portion. Thus, it is possible to make it easy to improve the driving efficiency of the rotation device.

[0014] In the above-described structure, the rotation device includes another mechanism portion that is provided on the outside of the second rotation body, the other mechanism portion transmits power to the mechanism portion, and the hole portion is provided at a position that is exposed from the other mechanism portion in the axial direction.

[0015] In the above-described structure, the second rotation body includes a first wall portion and a second wall portion that face each other on both sides in the axial direction with the housing portion interposed therebetween, and the hole portion includes a first hole portion that is provided on the first wall portion and a second hole portion that is provided on the second wall portion.

[0016] In the above-described structure, the first hole portion is disposed at a position that is on an inner side in the radial direction than the second hole portion.

[0017] In the above-described structure, the rotation device includes a plurality of the first hole portions and a plurality of the second hole portions, and the first hole portions and the second hole portions are respectively arranged in a circumferential direction with the rotation axis as a center.

[0018] In the above structure, the rotating device has a housing covering the second rotating body, has another housing portion partitioned by the housing and the second rotating body, the other mechanism portion is housed in the other housing portion, and the hole portion communicates with the other housing portion.

[0019] In the above structure, the first rotating body has an inner tooth on an inner peripheral surface, the second rotating body has a first gear frame and a second gear frame facing each other in the axial direction, the mechanism portion includes a crankshaft rotatably supported by the first gear frame and the second gear frame, and an external gear housed in the housing portion and rotatably supported by the crankshaft, engaged with the inner tooth, and the hole portion is disposed close to the inner tooth.

[0020] In the above structure, the hole portion has a first hole portion provided in the first gear frame and a second hole portion provided in the second gear frame, and the first hole portion is disposed at a position radially inward of the second hole portion.

[0021] Effects of the Invention

[0022] The above gear device can easily improve the driving efficiency. BRIEF DESCRIPTION OF DRAWINGS

[0023] Figure 1 is a sectional view of a driving device in an embodiment of the present application.

[0024] Figure 2 is a II view of Figure 1

[0025] Figure 3 is a sectional view along the III-III line of Figure 2

[0026] Figure 4 is an exploded perspective view of a second main bearing in an embodiment of the present application.

[0027] Figure 5 is a V portion enlarged view of Figure 3

[0028] Figure 6 is a VI view of Figure 1

[0029] Explanation of Reference Numerals

[0030] ​​​​1, speed reducer (rotating device); 2, housing (1st rotating body); 3, gear carrier (2nd rotating body); 5, inner tooth pin (mechanism part, inner gear); 7, base plate part (1st wall part, 1st gear carrier); 8, end plate part (2nd wall part, 2nd gear carrier); 13, crankshaft (mechanism part); 15, 1st outer gear (mechanism part, outer gear); 16, 2nd outer gear (mechanism part, outer gear); 41, 1st main bearing (rolling bearing); 42, 2nd main bearing (rolling bearing); 43, outer ring; 44, inner ring; 45, rolling element; 50, retainer; 63, base plate side lubricant inflow hole (hole part, 1st hole part); 64, end plate side lubricant inflow hole (hole part, 2nd hole part); 65, housing part; 70, housing; 74, lubricant storage part (other housing part); 80, input shaft (mechanism part); 80b, outer tooth (other mechanism part); 85, inner mechanism part (mechanism part); 86, outer mechanism part (other mechanism part); 105, motor spur gear (other mechanism part); A1, 1st rotation axis (rotation axis); Ds, minimum opening width of base plate side lubricant inflow hole; De, minimum opening width of end plate side lubricant inflow hole; G1, 1st gap; G2, 2nd gap. DETAILED DESCRIPTION

[0031] Next, an embodiment of the present application will be described based on the drawings.

[0032] <Driving device>

[0033] Figure 1 is a sectional view of a driving device 100 using a speed reducer 1 as a rotating device.

[0034] As shown in Figure 1 , the driving device 100 is provided with: the speed reducer 1; and an electric motor 101 and a driven member 102 which are linked to the speed reducer 1 and are arranged on both sides with the speed reducer 1 in between.

[0035] The electric motor 101 is provided with: a motor main body 103, a motor shaft 104 which extends from the motor main body 103, and a motor spur gear 105 which is provided to the motor shaft 104. The motor main body 103 is, for example, a brushless motor or the like. However, it is not limited thereto, and the motor main body 103 can generate a rotational force. For example, a hydraulic motor or the like can be used as the motor main body 103.

[0036] The motor main body 103 is mounted to a housing 70 of the speed reducer 1 which will be discussed later. The motor shaft 104 protrudes toward the speed reducer 1 through the housing 70. The motor spur gear 105 is provided to a tip end of the motor shaft 104 which protrudes.

[0037] The driven member 102 is, for example, an arm of a coordinated robot 106. The coordinated robot 106 refers to a "robot that cooperates with a work operator" in the field of factory automation (FA) and the like.

[0038] <Speed reduction device>

[0039] Figure 2 is Figure 1 II view. Figure 3 is a cross-sectional view along Figure 2 III-III line of the speed reduction device 1.

[0040] As shown in Figures 1 to 3 , the speed reduction device 1 reduces the rotation of the electric motor 101 and outputs. The speed reduction device 1 is a so-called eccentric swing type speed reduction device. The speed reduction device 1 has a cylindrical housing 2, a gear carrier 3 rotatably provided on the inner side of the housing 2 in the radial direction, and a speed reduction mechanism 4 coupled to the gear carrier 3. The central axis of the housing 2 coincides with the rotational axis of the gear carrier 3.

[0041] In the following description, as a general name of these central axes and rotational axes, the first rotational axis A1 is referred to. The direction parallel to the first rotational axis A1 is referred to as the axial direction. The rotational direction of the gear carrier 3 is referred to as the circumferential direction. The radial direction of the housing 2 orthogonal to the axial direction and the circumferential direction is simply referred to as the radial direction. The central side of the axial direction of the housing 2 is referred to as the central side of the axial direction. The side opposite to the central side of the axial direction is referred to as the outer side of the axial direction.

[0042] <Housing>

[0043] The housing 2 is formed of, for example, spheroidal graphite cast iron (ductile cast iron). For example, FCD450 is used as the spheroidal graphite cast iron. An outer flange portion 2a that protrudes to the outer side in the radial direction is integrally formed on the outer peripheral surface of the housing 2. A plurality of bolt holes 2b are formed in the outer flange portion 2a. The bolt holes 2b are arranged at equal intervals in the circumferential direction. A bolt not shown is inserted into the bolt holes 2b, and the bolt is fastened to the driven member 102 to fix the speed reduction device 1.

[0044] A portion of the outer peripheral surface of the housing 2 on the electric motor 101 side from the outer flange portion 2a functions as an insertion portion 2e for insertion of an outer case 70 to be described later. An O-ring groove 2f is formed on the entire circumference in the insertion portion 2e. An O-ring not shown is installed in the O-ring groove 2f. Thereby, the sealing property between the housing 2 and the outer case 70 is ensured.

[0045] A plurality of pin grooves 2c along the axial direction are formed in the inner peripheral surface 2d of the housing 2. The pin grooves 2c are arranged at equal intervals in the circumferential direction. An inner tooth pin 5 is respectively inserted into each of the pin grooves 2c. The inner tooth pin 5 functions as an inner tooth that engages with outer gears 15 and 16 to be described later of the speed reduction mechanism 4.

[0046] On the inner peripheral surface 2d of the housing 2, on both sides in the axial direction of the pin groove 2c, housing bearing holding surfaces 22a, 22b (first housing bearing holding surface 22a, second housing bearing holding surface 22b) are formed by means of step surfaces 21a, 21b (first step surface 21a, second step surface 21b), respectively. Each of the housing bearing holding surfaces 22a, 22b is formed in a ring shape at a position that is radially outward of the pin groove 2c. The first housing bearing holding surface 22a among the two housing bearing holding surfaces 22a, 22b is provided with the first main bearing 41. The second housing bearing holding surface 22b among the two housing bearing holding surfaces 22a, 22b is provided with the second main bearing 42.

[0047] <MAIN BEARING>

[0048] Each of the main bearings 41, 42 is of the same structure and is arranged symmetrically about the center in the axial direction of the housing 2. Therefore, in the following description, only the second main bearing 42 will be described, and the detailed description of the first main bearing 41 will be omitted by using the same reference numerals as those of the second main bearing 42.

[0049] Figure 4 is an exploded perspective view of the second main bearing 42. Figure 5 is an enlarged view of the V portion of Figure 3

[0050] As shown in Figures 3 to 5 , the second main bearing 42 is a so-called tapered roller bearing. The second main bearing 42 includes an outer ring 43 that is fitted to the second housing bearing holding surface 22b, an inner ring 44 that is arranged radially inward of the outer ring 43, a plurality of rolling elements 45 that are arranged between the outer ring 43 and the inner ring 44, and a retainer 50 that holds the plurality of rolling elements 45 at equal intervals in the circumferential direction.

[0051] The outer ring 43 is formed in a circular ring shape with the first rotation axis Al as the center. The cross section of the outer ring 43 in the axial direction is formed in a triangular shape. The end surface 43a of the outer ring 43 on the central side in the axial direction abuts against the corresponding step surface 21a, 21b. Thus, the positioning of each of the main bearings 41, 42 in the axial direction with respect to the housing 2 is performed.

[0052] An outer ring raceway surface 43b that is inclined with respect to the axial direction is formed on the inner peripheral surface of the outer ring 43. Specifically, the outer ring raceway surface 43b is formed so as to be inclined in such a manner that the inner diameter gradually increases toward the outer side in the axial direction. Such an outer ring 43 of each of the main bearings 41, 42 is located at a position that is on the central side in the axial direction of the inner ring 44.

[0053] ​The inner ring 44 is integrally formed with an inner ring main body 46 having a triangular cross section in the axial direction and a protrusion 47 protruding toward the axial center from an end portion of the inner ring main body 46 on the central side in the axial direction. An inner peripheral surface 46a of the inner ring main body 46 and an inner peripheral surface 47a of the protrusion 47 are on the same plane and parallel to the axial direction. An outer peripheral surface 47b of the protrusion 47 is also parallel to the axial direction.

[0054] An inner ring raceway surface 46b inclined with respect to the axial direction is formed on an outer peripheral surface of the inner ring main body 46. Specifically, the inner ring raceway surface 46b is formed so as to be inclined in such a manner that an outer diameter gradually increases toward the outer side in the axial direction. The inner ring raceway surface 46b faces the outer ring raceway surface 43b.

[0055] A flange portion 48 protruding toward the outer side in the radial direction is integrally formed on an outer side end of the inner ring raceway surface 46b in the axial direction. The flange portion 48 protrudes toward the outer side in the axial direction with respect to the outer ring 43. A cross section of the flange portion 48 in the axial direction has a triangular shape. That is, the flange portion 48 has a flange inner peripheral surface 48a connected to the inner ring raceway surface 46b and a flange outer peripheral surface 48b facing the outer side in the radial direction. The flange inner peripheral surface 48a is orthogonal to the inner ring raceway surface 46b. The flange outer peripheral surface 48b is parallel to the axial direction.

[0056] Each of the rolling elements 45 is a conical roller having a circular conical frustum shape. A central axis A2 of each of the rolling elements 45 is inclined with respect to the axial direction in such a manner as to follow an inclination direction of the outer ring raceway surface 43b and the inner ring raceway surface 46b. Each of the rolling elements 45 is arranged at equal intervals in the circumferential direction. Each of the rolling elements 45 is restricted from moving in the direction of the central axis A2 by abutting against the flange inner peripheral surface 48a with an end surface 45a on the outer side in the axial direction. Thus, each of the rolling elements 45 revolves around the first rotation axis Al while rolling on the outer ring raceway surface 43b and the inner ring raceway surface 46b.

[0057] The retainer 50 is integrally formed with a small-diameter ring 51 arranged at a position on the central side in the axial direction than the rolling elements 45, a large-diameter ring 52 arranged at a position on the outer side in the axial direction than the rolling elements 45, and a plurality of column portions 53 linking the small-diameter ring 51 and the large-diameter ring 52. The small-diameter ring 51 is located between the outer ring raceway surface 43b and the inner peripheral surface 47a of the protrusion 47 of the inner ring 44 in the radial direction. The large-diameter ring 52 opposes the flange outer peripheral surface 48b in the radial direction. The large-diameter ring 52 is located at a position on the outer side in the axial direction than the outer ring 43.

[0058] The column portions 53 extend in the axial direction and the radial direction and are arranged at equal intervals in the circumferential direction. The rolling elements 45 are arranged in recesses 54 respectively divided by the column portions 53, the small-diameter ring 51, and the large-diameter ring 52. Thus, the rolling elements 45 are held by the retainer 50.

[0059] Each main bearing 41 or 42 has a first gap G1 formed between the outer ring 43 and the retainer 50, and a second gap G2 formed between the inner ring 44 and the retainer 50. More specifically, the first gap G1 refers to the gap between the outer ring raceway surface 43b and the column portion 53. The width of the first gap G1 refers to the width between the outer ring raceway surface 43b and the column portion 53. The second gap G2 refers to the gap between the flange outer circumferential surface 48b and the large-diameter ring 52. The width of the second gap G2 refers to the width between the flange outer circumferential surface 48b and the large-diameter ring 52. In other words, the width between the outer ring 43 and the retainer 50 and the width between the inner ring 44 and the retainer 50 refer to the axially outer widths of the two axially oriented sides of each main bearing 41 or 42.

[0060] The carrier 3 is rotatably supported by the housing 2 via the main bearings 41 and 42 .

[0061] <Gear rack>

[0062] The gear carrier 3 includes a disc-shaped base plate portion (an example of the first gear carrier in the claims) 7 and an end plate portion (an example of the second gear carrier in the claims) 8, which are arranged axially opposite to each other. The base plate portion 7 and the end plate portion 8 are formed, for example, from spheroidal graphite cast iron (ductile iron). For example, FCD450 is used as the spheroidal graphite cast iron.

[0063] <Substrate part>

[0064] Figure 6 yes Figure 1 VI direction view.

[0065] like Figure 3 、 Figure 6 As shown, the base plate portion 7 is formed in a disk shape. A base plate bearing retaining surface 7c is formed on the outer peripheral surface 7a of the base plate portion 7 at a location radially opposed to the first housing bearing retaining surface 22a. The base plate bearing retaining surface 7c is formed into an annular shape radially inward of the outer peripheral surface 7a via a step portion 7b.

[0066] The inner ring 44 of the first main bearing 41 fits into the base plate bearing retaining surface 7c. The axially outer end surface 44a of the inner ring 44 of the first main bearing 41 abuts against the stepped portion 7b. This axial positioning of the first main bearing 41 relative to the base plate 7 is achieved.

[0067] A seal portion 24 is provided between the outer peripheral surface 7a of the base plate 7 and the inner peripheral surface 2d of the housing 2, on the opposite side of the end plate 8 from the first main bearing 41. The seal portion 24 ensures sealing between the base plate 7 and the housing 2.

[0068] A substrate shaft insertion hole 7d is formed in the center in the radial direction of the substrate portion 7. A shaft bearing 20 is provided in the substrate shaft insertion hole 7d. The shaft bearing 20 is, for example, a tapered roller bearing.

[0069] A plurality of (for example, three in the present embodiment) crank shaft insertion recesses 7e are formed around the substrate shaft insertion hole 7d of the substrate portion 7. Each of the crank shaft insertion recesses 7e is formed in a first end surface 7f of the substrate portion 7 on the side of the end plate portion 8. The crank shaft insertion recesses 7e are arranged at equal intervals in the circumferential direction. A crank shaft bearing 18 is provided in each of the crank shaft insertion recesses 7e. The crank shaft bearing 18 is, for example, a tapered roller bearing.

[0070] Three column portions 9 are formed protruding toward the end plate portion 8 in the first end surface 7f of the substrate portion 7. The column portions 9 are formed in a triangular prism shape in which the width in the circumferential direction as viewed in the axial direction increases toward the outside in the radial direction. Each of the column portions 9 is arranged between the crank shaft insertion recesses 7e adjacent in the circumferential direction. The three column portions 9 are arranged at equal intervals in the circumferential direction.

[0071] Three internal thread portions 26 are formed in the top end surface 9a of each of the column portions 9. The three internal thread portions 26 are arranged in each of the corner portions of the column portion 9 as viewed in the axial direction. One dowel hole 27 is formed in the top end surface 9a of each of the column portions 9. The dowel hole 27 is arranged between two of the internal thread portions 26 adjacent in the circumferential direction on the outside in the radial direction of the top end surface 9a of the column portion 9. These internal thread portions 26 and dowel holes 27 are used to integrate the substrate portion 7 and the end plate portion 8 (details will be discussed later).

[0072] A recess 61 is formed in the center in the radial direction of a second end surface 7g of the substrate portion 7 on the side opposite the end plate portion 8. The recess 61 is formed in a circular shape as viewed in the axial direction. A plurality of mounting holes 59 are formed in the outer peripheral portion of the second end surface 7g of the substrate portion 7. The mounting holes 59 are arranged at equal intervals in the circumferential direction. The driven member 102 (refer to Figure 1 ) is mounted to the second end surface 7g of the substrate portion 7 using each of the mounting holes 59.

[0073] A crank shaft through hole 62 is formed in the center in the radial direction of each of the crank shaft insertion recesses 7e of the substrate portion 7. The crank shaft through hole 62 penetrates the substrate portion 7 in the axial direction and communicates with each of the crank shaft insertion recesses 7e and the recess 61.

[0074] A plurality of (for example, three in the present embodiment) substrate-side lubricant inflow holes 63 are formed in the substrate portion 7. The substrate-side lubricant inflow holes 63 are arranged at a certain interval in the circumferential direction around the substrate shaft insertion hole 7d. That is, the substrate-side lubricant inflow holes 63 are arranged at a certain interval in the circumferential direction with the first rotation axis Al as the center. More specifically, the substrate-side lubricant inflow holes 63 are arranged at a position radially inward of the crank shaft through holes 62 and between two crank shaft through holes 62 adjacent in the circumferential direction. The substrate-side lubricant inflow holes 63 pass through the substrate portion 7 in the axial direction and communicate with the second end surface 7g of the substrate portion 7 and the recess 61.

[0075] The substrate-side lubricant inflow holes 63 are also formed in a circular shape as viewed in the axial direction. The minimum opening width Ds of the substrate-side lubricant inflow holes 63 is larger than the width of the first gap Gl and the width of the second gap G2 in each main bearing 41, 42. The minimum opening width Ds of the substrate-side lubricant inflow holes 63 refers to the width of the substrate-side lubricant inflow holes 63 orthogonal to the direction of the axis Ahs and is the smallest width among the widths. The substrate-side lubricant inflow holes 63 are also formed in a circular shape as viewed in the axial direction, and thus the minimum opening width Ds of the substrate-side lubricant inflow holes 63 is the same as the diameter of the substrate-side lubricant inflow holes 63.

[0076] <End plate portion>

[0077] Return Figure 2 , Figure 3 The end plate portion 8 is formed in a circular plate shape. An end plate bearing holding surface 8c is formed at a position of the outer circumferential surface 8a radially opposite to the second housing bearing holding surface 22b in the radial direction. The end plate bearing holding surface 8c is formed in a ring shape at a position radially inward of the outer circumferential surface 8a by means of the step portion 8b.

[0078] The inner ring 44 of the second main bearing 42 is fitted to the end plate bearing holding surface 8c. The end surface 44a of the inner ring 44 of the second main bearing 42 on the outer side in the axial direction abuts against the step portion 8b with the gasket 66 interposed therebetween. Thus, the positioning of the second main bearing 42 in the axial direction with respect to the end plate portion 8 is performed.

[0079] An end plate shaft insertion hole 8d is formed in the radial center of the end plate portion 8. The end plate shaft insertion hole 8d is arranged coaxially with the substrate shaft insertion hole 7d. The shaft bearing 20 is provided in the end plate shaft insertion hole 8d as well as in the substrate shaft insertion hole 7d.

[0080] A plurality of (for example, three in the present embodiment) crank insertion holes 8e are formed around the end plate shaft insertion hole 8d of the end plate portion 8. The respective crank insertion holes 8e are arranged at equal intervals in the circumferential direction. The respective crank insertion holes 8e are arranged coaxially with the crank insertion recesses 7e of the base plate portion 7. That is, the center axes A2 of the crank insertion holes 8e and the crank insertion recesses 7e, which are axially opposite to each other, are parallel to the first rotation axis Al. Crank bearings 18 are provided in the respective crank insertion holes 8e as well as in the respective crank insertion recesses 7e.

[0081] In the end plate portion 8, three bolt insertion holes 76 and end plate pin holes 77 are formed at positions opposite to the column portions 9 of the base plate portion 7 in the axial direction, respectively. The three bolt insertion holes 76 are arranged coaxially with the internally threaded portions 26 of the column portions 9. The end plate pin holes 77 are arranged coaxially with the column pin holes 27.

[0082] The bolts 91 are inserted into the three bolt insertion holes 76 from the side opposite to the base plate portion 7, and the respective bolts 91 are fastened to the internally threaded portions 26. The pins 92 are inserted or pressed into the end plate pin holes 77 and the column pin holes 27. Thus, the end plate portion 8 is fixed to the base plate portion 7 on the basis of the positioning between the base plate portion 7 and the end plate portion 8 being performed with high precision.

[0083] In a state where the end plate portion 8 is fixed to the base plate portion 7, a receiving portion 65 is formed between the base plate portion 7 and the end plate portion 8. The receiving portion 65 has a width corresponding to the height of the column portions 9, and is formed by the base plate portion 7, the end plate portion 8, and the housing 2. In other words, the receiving portion 65 is located between the first main bearing 41 provided in the base plate portion 7 and the second main bearing 42 provided in the end plate portion 8.

[0084] A plurality of (for example, three in the present embodiment) end plate side lubricant inflow holes 64 are formed in the end plate portion 8. The end plate side lubricant inflow holes 64 are arranged at equal intervals in the circumferential direction with the first rotation axis Al as the center. More specifically, the end plate side lubricant inflow holes 64 are arranged at positions on the outer circumferential portion of the end plate portion 8 and on the radially inner side of the second main bearing 42 at equal intervals in the circumferential direction.

[0085] The end plate side lubricant inflow holes 64 are arranged in the vicinity of the second main bearing 42 and in the vicinity of the radially outer corner of the column portion 9 of the base plate portion 7 as viewed in the axial direction. In other words, the end plate side lubricant inflow holes 64 are arranged in the radial direction in line with the second main bearing 42. Thus, the end plate side lubricant inflow holes 64 are arranged at positions radially outward of the base plate side lubricant inflow holes 63. The end plate side lubricant inflow holes 64 are arranged in the vicinity of the inner tooth pin 5 of the housing 2.

[0086] The end plate side lubricant inflow hole 64 penetrates the end plate portion 8 in the axial direction and communicates with the accommodation portion 65. The end plate side lubricant inflow hole 64 is also formed in a circular shape as viewed in the axial direction. The minimum opening width De of the end plate side lubricant inflow hole 64 is larger than the width of the first gap Gl and the width of the second gap G2 in each main bearing 41, 42. The minimum opening width De of the end plate side lubricant inflow hole 64 refers to the width of the end plate side lubricant inflow hole 64 orthogonal to the direction of the axis Ahe, and is the smallest width among the widths. The end plate side lubricant inflow hole 64 is also formed in a circular shape as viewed in the axial direction, and thus the minimum opening width De of the end plate side lubricant inflow hole 64 is the same as the diameter of the end plate side lubricant inflow hole 64.

[0087] <Speed reduction mechanism>

[0088] The speed reduction mechanism 4 reduces the rotation of the electric motor 101 at a certain ratio to rotate the gear carrier 3. The speed reduction mechanism 4 mainly includes an input shaft 80 inserted into the base plate shaft insertion hole 7d and the end plate shaft insertion hole 8d, an input spur gear 82 provided to the input shaft 80, three crankshafts 13 inserted into the crankshaft insertion recesses 7e of the base plate portion 7 and the crankshaft insertion holes 8e of the end plate portion 8, respectively, transmission spur gears 14 provided to the crankshafts 13, and two external gears 15, 16 (a first external gear 15 and a second external gear 16) provided between the base plate portion 7 and the end plate portion 8.

[0089] The input shaft 80 is rotatably supported to the gear carrier 3 (the base plate portion 7 and the end plate portion 8) by the shaft bearings 20. The end portion 80a of the input shaft 80 on the end plate portion 8 side protrudes outward in the axial direction from the end plate portion 8. An external tooth 80b is formed on the protruding end portion 80a of the input shaft 80.

[0090] A support shaft 81 protruding outward in the axial direction is integrally formed on the end portion 80a of the input shaft 80. The support shaft 81 is coaxially arranged with the input shaft 80. The diameter of the support shaft 81 is smaller than the diameter of the input shaft 80. The input spur gear 82 is fitted and fixed to the support shaft 81.

[0091] An external tooth 82a is formed on the outer peripheral portion of the input spur gear 82. The external tooth 82a is engaged with the motor spur gear 105 of the electric motor 101. Thus, the input shaft 80 rotates in accordance with the rotation of the motor shaft 104.

[0092] The crankshafts 13 are rotatably supported to the gear carrier 3 (the base plate portion 7 and the end plate portion 8) by the crankshaft bearings 18. The crankshafts 13 have shaft bodies 13c that rotate about a center axis A2 and first and second eccentric portions 13a, 13b formed in the center in the axial direction of the shaft bodies 13c. Hereinafter, the center axis A2 is referred to as the second rotation axis A2 of the crankshafts 13.

[0093] The both sides in the axial direction of the shaft body 13c are rotatably supported to the gear carrier 3 (the base plate portion 7 and the end plate portion 8) by the crankshaft bearings 18. The end portion 13d of the shaft body 13c on the end plate portion 8 side protrudes to the outside in the axial direction of the end plate portion 8 via the crankshaft bearing 18.

[0094] The first eccentric portion 13a and the second eccentric portion 13b are eccentric with respect to the second rotation axis A2. The first eccentric portion 13a and the second eccentric portion 13b are arranged adjacent to each other in the axial direction between the two crankshafts 18. In other words, the first eccentric portion 13a and the second eccentric portion 13b are arranged adjacent to each other in the axial direction between the base plate portion 7 and the end plate portion 8. The first eccentric portion 13a and the second eccentric portion 13b are arranged with a phase angle of 180° deviated.

[0095] The inner peripheral surfaces of the roller bearings 19 are fitted to the respective eccentric portions 13a, 13b. The roller bearings 19 are, for example, cylindrical roller bearings. The first outer gear 15 and the second outer gear 16 are rotatably supported to the respective crankshafts 13 by the roller bearings 19.

[0096] The first outer gear 15 and the second outer gear 16 are arranged in the accommodation portion 65. The first outer gear 15 and the second outer gear 16 overlap in the axial direction. Through-holes 15a, 16a are formed in the first outer gear 15 and the second outer gear 16. The outer peripheral surfaces of the roller bearings 19 are fitted to the respective through-holes 15a, 16a. Thus, if the first eccentric portion 13a and the second eccentric portion 13b swing and rotate due to the rotation of the crankshafts 13, the first outer gear 15 and the second outer gear 16 swing and rotate by the roller bearings 19.

[0097] Openings 15b, 16b for avoiding interference with the column portions 9 are formed in the first outer gear 15 and the second outer gear 16. Axial insertion holes 15c, 16c are formed in the central portions in the radial direction of the first outer gear 15 and the second outer gear 16. Outer teeth 15d, 16d are formed in the outer peripheral portions of the first outer gear 15 and the second outer gear 16, respectively. The number of teeth of the respective outer teeth 15d, 16d is one less than the number of the inner teeth 5 of the housing 2.

[0098] The transfer spur gears 14 are fitted and fixed to the end portions 13d of the respective crankshafts 13 (the respective shaft bodies 13c). The shaft bodies 13c and the transfer spur gears 14 are arranged coaxially and integrated. Outer teeth 17 are formed in the outer peripheral portions of the transfer spur gears 14. The outer teeth 17 are engaged with the outer teeth 80b of the input shaft 80.

[0099] Thus, the reduction mechanism 4 is roughly divided into an internal mechanism portion (one example of the mechanism portion in the claim) 85 housed inside the inside (housing portion 65) of the gear housing 3 and an external mechanism portion (one example of the other mechanism portion in the claim) 86 provided outside the gear housing 3. The internal mechanism portion 85 is provided with the inner tooth pin 5, each crankshaft 13, each outer gear 15, 16, and the input shaft 80. The external mechanism portion 86 is provided with the external teeth 80b of the input shaft 80, the input spur gear 82, and the transmission spur gear 14.

[0100] As described in detail in Figure 2 Thus, the end plate side lubricant inflow hole 64 formed in the end plate portion 8 of the gear housing 3 is exposed from the external mechanism portion 86 as viewed in the axial direction. More specifically, the end plate side lubricant inflow hole 64 is disposed at a position where the outer periphery of the end plate side lubricant inflow hole 64 and the outer periphery of the transmission spur gear 14 slightly overlap as viewed in the axial direction.

[0101] <Shell>

[0102] Returning to Figure 1 The shell 70 is provided on the end plate portion 8 side of such a reduction device 1 in a manner so as to cover the end plate portion 8. The shell 70 is formed in a bottomed cylindrical shape and is provided with a peripheral wall portion 71 and a bottom wall portion 72.

[0103] The peripheral wall portion 71 is formed in a stepped shape. The peripheral wall portion 71 has a large-diameter peripheral wall 71a provided on the opening portion 70a side of the shell 70, a stepped portion 71b formed in the bottom wall portion 72 of the large-diameter peripheral wall 71a, and a small-diameter peripheral wall 71c connected to the large-diameter peripheral wall 71a by the stepped portion 71b. The outer diameter of the small-diameter peripheral wall 71c is smaller than the outer diameter of the large-diameter peripheral wall 71a.

[0104] An outer flange portion 73 extending to the outer side in the radial direction is formed at the top end of the large-diameter peripheral wall 71a on the side opposite the bottom wall portion 72. The inner peripheral surface of the large-diameter peripheral wall 71a is fitted to the fitting portion 2e of the housing 2 in a manner so that the opening portion 70a faces the reduction device 1 side. At this time, the outer flange portion 73 of the shell 70 abuts against the outer flange portion 2a of the housing 2. Thus, the housing 2 and the shell 70 are positioned in the axial direction. By the fitting of the large-diameter peripheral wall 71a to the housing 2, a lubricant storage portion 74 partitioned by the shell 70, the housing 2, and the end plate portion 8 is formed inside the shell 70.

[0105] On the bottom wall portion 72, the electric motor 101 is mounted on the side opposite the reduction mechanism 4. On the bottom wall portion 72, a shaft insertion hole 72a is formed so as to pass through the portion where the electric motor 101 is mounted. The motor shaft 104 is inserted into this shaft insertion hole 72a. Thus, the motor shaft 104 protrudes toward the reduction device 1 via the shell 70.

[0106] In the bottom wall portion 72, in addition to the shaft insertion hole 72a, a lubricant injection hole 72b is also formed so as to penetrate therethrough. The lubricant L is injected into the lubricant accumulation portion 74 via the lubricant injection hole 72b (indicated by a hatched line in Figure 1 ).

[0107] < Lubricant Filling Path >

[0108] Next, the lubricant filling path will be described. Figure 1

[0109] The lubricant L injected into the lubricant accumulation portion 74 flows into the accommodation portion 65 via the end plate side lubricant inflow hole 64 (refer to arrow Y1 in Figure 1 ). At this time, as the inflow path of the lubricant from the lubricant accumulation portion 74 to the inside (accommodation portion 65) of the gear carrier 3, in addition to the end plate side lubricant inflow hole 64, the first gap G1 and the second gap G2 of the second main bearing 42 can also be cited (refer to Figure 5 ). However, the minimum opening width De of the end plate side lubricant inflow hole 64 is larger than the width of the first gap G1 and the width of the second gap G2. Therefore, the lubricant L actively flows into the accommodation portion 65 via the end plate side lubricant inflow hole 64.

[0110] Furthermore, the end plate side lubricant inflow hole 64 is exposed from the outside mechanism portion 86 (transmission spur gear 14) as viewed in the axial direction. Therefore, for example, compared to a case in which the end plate side lubricant inflow hole 64 is formed at a position inside the transmission spur gear 14, the resistance at the time of inflow of the lubricant L into the end plate side lubricant inflow hole 64 is reduced. As a result, the lubricant L smoothly flows into the end plate side lubricant inflow hole 64.

[0111] The end plate side lubricant inflow hole 64 is arranged at a position on the outer peripheral portion of the end plate portion 8 and radially inward of the second main bearing 42 at a certain interval in the circumferential direction. That is, the end plate side lubricant inflow hole 64 is arranged close to the inner tooth pin 5 of the housing 2. As a result, the lubricant L that flows into the accommodation portion 65 is sequentially filled from the vicinity of the inner tooth pin 5 into the accommodation portion 65. Therefore, the lubricant L is actively applied to the meshing portions of the inner tooth pin 5, the external teeth 15d, 16d of each of the external gears 15, 16.

[0112] ​The substrate-side lubricant inflow hole 63 formed in the substrate portion 7 functions as an air discharge portion when the lubricant L flowing into the accommodation portion 65. The minimum opening width Ds of the substrate-side lubricant inflow hole 63 is also larger than the widths of the first gap G1 and the second gap G2 in the first main bearing 41. Therefore, air is more actively discharged from the substrate-side lubricant inflow hole 63 than from these first and second gaps G1 and G2. As a result, the lubricant L smoothly flows into the accommodation portion 65. If the accommodation portion 65 is filled with the lubricant L, the lubricant L also flows into the substrate-side lubricant inflow hole 63 (see arrow Y2 in FIG. 6). Figure 1

[0113] The end plate-side lubricant inflow hole 64 is disposed at a position radially outward of the substrate-side lubricant inflow hole 63. Therefore, compared to a case in which the end plate-side lubricant inflow hole 64 and the substrate-side lubricant inflow hole 63 are disposed coaxially, the path from the end plate-side lubricant inflow hole 64 to the substrate-side lubricant inflow hole 63 becomes complex. As a result, the lubricant L spreads throughout the gear carrier 3 without missing.

[0114] <Operation of the speed reduction device>

[0115] Next, the operation of the speed reduction device 1 will be described.

[0116] A portion of the external teeth 15d, 16d of each of the external gears 15, 16 meshes with the internal tooth pin 5 of the housing 2. In this state, if the electric motor 101 is driven, the rotation of the motor shaft 104 is transmitted to the input shaft 80 via the motor spur gear 105 and the input spur gear 82. Thus, the input shaft 80 rotates.

[0117] With the rotation of the input shaft 80, each of the transmission spur gears 14 that meshes with the external teeth 80b of the input shaft 80 rotates. Each of the crankshafts 13 rotates around the second rotation axis A2 integrally with these transmission spur gears 14.

[0118] Thus, each of the external gears 15, 16 oscillatory rotates. The number of teeth of each of the external teeth 15d, 16d is, for example, one less than the number of the internal tooth pin 5. Therefore, the meshing positions of each of the external teeth 15d, 16d are sequentially circumferentially offset with respect to the internal tooth pin 5 (housing 2), and each of the external gears 15, 16 rotates on its own axis. The rotation thereof is decelerated with respect to the rotation of the crankshaft 13.

[0119] With the rotation of each of the external gears 15, 16, each of the crankshafts 13 also revolves around the first rotation axis Al while oscillatory rotating around the second rotation axis A2. Each of the crankshafts 13 is rotatably supported to the gear carrier 3 (substrate portion 7, end plate portion 8). Therefore, the gear carrier 3 rotates with the revolution of each of the crankshafts 13. The speed reduction device 1 (inside the housing 2, inside the gear carrier 3) is filled with the lubricant L, and thus the gear carrier 3 can be smoothly rotated.​

[0120] The reduction device 1 reduces the rotation of the electric motor 101 and outputs to the driven member 102 due to the rotation of the gear carrier 3. Thereby, the driven member 102 is driven. In a case where the driven member 102 is assumed to be fixed, the reduction device 1 can reduce the rotation of the electric motor 101 and output from the housing 2.

[0121] Thus, in the gear carrier 3 of the above-described reduction device 1, the substrate-side lubricant inflow hole 63 and the end plate-side lubricant inflow hole 64 that communicate with the accommodation portion 65 of the outside and the inside of the gear carrier 3 are formed. Therefore, for example, the lubricant L can be easily caused to flow into the inside of the gear carrier 3 via the end plate-side lubricant inflow hole 64.

[0122] Further, the minimum opening width Ds of the substrate-side lubricant inflow hole 63 and the minimum opening width De of the end plate-side lubricant inflow hole 64 are each larger than the width of the first gap G1 and the width of the second gap G2 in each main bearing 41, 42. Therefore, for example, the lubricant L can be more actively injected from the end plate-side lubricant inflow hole 64 than the first gap G1 and the second gap G2 of each main bearing 41, 42. Thus, it is possible to make it easy to improve the driving efficiency of the reduction device 1.

[0123] The end plate-side lubricant inflow hole 64 is exposed from the outside mechanism portion 86 in the axial direction. Thus, even in the reduction device 1 provided with the outside mechanism portion 86, it is possible to prevent the lubricant L from being hindered from being injected into the substrate-side lubricant inflow hole 63 by the outside mechanism portion 86. Therefore, it is possible to more actively inject the lubricant L from the substrate-side lubricant inflow hole 63.

[0124] The substrate portion 7 and the end plate portion 8 that constitute the gear carrier 3 are disposed on both sides in the axial direction with the accommodation portion 65 interposed therebetween. The substrate-side lubricant inflow hole 63 and the end plate-side lubricant inflow hole 64 are formed in the substrate portion 7 and the end plate portion 8, respectively. Therefore, in a case where the lubricant L is caused to flow into the accommodation portion 65 via the substrate-side lubricant inflow hole 63, it is possible to cause the substrate-side lubricant inflow hole 63 to have a function as an air discharge portion. By discharging air from the substrate-side lubricant inflow hole 63, it is possible to cause the lubricant L to smoothly flow into the accommodation portion 65.

[0125] The end plate-side lubricant inflow hole 64 is disposed at a position that is radially outward of the substrate-side lubricant inflow hole 63. Therefore, compared to a case where the end plate-side lubricant inflow hole 64 and the substrate-side lubricant inflow hole 63 are disposed on the same axis, it is possible to make the path from the end plate-side lubricant inflow hole 64 to the substrate-side lubricant inflow hole 63 complex. As a result, it is possible to cause the lubricant L to permeate throughout the gear carrier 3 without omission.

[0126] Three of the substrate-side lubricant inflow holes 63 and three of the end plate-side lubricant inflow holes 64 are formed, respectively. The substrate-side lubricant inflow holes 63 and the end plate-side lubricant inflow holes 64 are arranged at a certain interval in the circumferential direction with the first rotational axis Al as the center. By using a plurality of the end plate-side lubricant inflow holes 64, the lubricant L can be rapidly and smoothly supplied to the accommodation portion 65.

[0127] The speed reduction device 1 is provided with a housing 70 that covers the end plate portion 8. A lubricant reservoir 74 is formed by the housing 70, the casing 2, and the end plate portion 8. The end plate-side lubricant inflow holes 64 communicate with the lubricant reservoir 74. Therefore, by filling the lubricant reservoir 74 with the lubricant L, the lubricant L can be injected to the accommodation portion 65 via the lubricant reservoir 74. Thus, the amount of the lubricant L sufficient for the speed reduction device 1 can be maintained, and the operation to improve the driving efficiency of the speed reduction device 1 can be further facilitated.

[0128] The end plate-side lubricant inflow holes 64 are arranged at a certain interval in the circumferential direction at a position on the outer peripheral portion of the end plate portion 8 and radially inward of the second main bearing 42. That is, the end plate-side lubricant inflow holes 64 are arranged close to the inner tooth pin 5 of the casing 2. As a result, the lubricant L supplied to the accommodation portion 65 can be sequentially filled from the vicinity of the inner tooth pin 5 into the accommodation portion 65. Therefore, the lubricant L can be actively applied to the meshing portions of the inner tooth pin 5 and the external teeth 15d, 16d of the respective external gears 15, 16. Thus, the driving efficiency of the speed reduction device 1 can be improved.

[0129] The present application is not limited to the above-described embodiments, and includes embodiments in which various modifications are made to the above-described embodiments without departing from the gist of the present application.

[0130] For example, in the above-described embodiments, the speed reduction device 1 of the so-called eccentric swing type is described as the rotational device. However, the present application is not limited thereto, and the structure of the speed reduction device 1 described above can be employed in various rotational devices in which two rotational bodies (the first rotational body and the second rotational body) are arranged to be rotatable relative to each other by means of a rolling bearing.

[0131] In the above-described embodiments, the case in which the speed reduction mechanism 4 is provided with two external gears 15, 16 is described. The case in which the speed reduction mechanism 4 is provided with three crankshafts 13 is described. However, the present application is not limited thereto, and the speed reduction mechanism 4 can be provided with at least one external gear. The number of the crankshafts 13 can also be plural.

[0132] In the above-described embodiments, the case in which the respective main bearings 41, 42 are so-called tapered roller bearings is described. However, the present application is not limited thereto, and various rolling bearings can be used as the respective main bearings 41, 42.

[0133] In the above-described embodiment, the case where the housing 2, the base plate portion 7, and the end plate portion 8 are each formed of spheroidal graphite cast iron has been described. For example, the case where FCD450 is used as the spheroidal graphite cast iron has been described. However, the present application is not limited thereto, and various materials can be used for the housing 2, the base plate portion 7, and the end plate portion 8.

[0134] In the above-described embodiment, the case where the base plate side lubricant inflow hole 63 and the end plate side lubricant inflow hole 64 are each formed in a circular shape as viewed in the axial direction has been described. However, the present application is not limited thereto, and the base plate side lubricant inflow hole 63 and the end plate side lubricant inflow hole 64 can also be formed in a shape other than a circular shape as viewed in the axial direction.

[0135] For example, in the case where the base plate side lubricant inflow hole 63 and the end plate side lubricant inflow hole 64 are each formed in an elliptical shape as viewed in the axial direction, the minimum opening width Ds, De of the base plate side lubricant inflow hole 63 and the end plate side lubricant inflow hole 64 refers to the length of the minor axis.

[0136] The base plate side lubricant inflow hole 63 and the end plate side lubricant inflow hole 64 can also be formed differently. In this case, the minimum opening width Ds, De of the base plate side lubricant inflow hole 63 and the end plate side lubricant inflow hole 64 refers to the minimum width as viewed in the direction extending from each lubricant inflow hole 63, 64 at the portion where the opening cross-sectional area of each lubricant inflow hole 63, 64 is the smallest.

[0137] In the above-described embodiment, the case where the base plate side lubricant inflow hole 63 and the end plate side lubricant inflow hole 64 are each formed, for example, with three holes has been described. The case where the base plate side lubricant inflow hole 63 is arranged around the base plate shaft insertion hole 7d at a certain interval in the circumferential direction has been described. The case where the end plate side lubricant inflow hole 64 is arranged at a position radially inward of the second main bearing 42 and around the outer peripheral portion of the end plate portion 8 at a certain interval in the circumferential direction has been described. However, the present application is not limited thereto, and the number and the position where the base plate side lubricant inflow hole 63 and the end plate side lubricant inflow hole 64 are formed can be arbitrarily determined.

[0138] In the above-described embodiment, the case where the housing 70 is provided on the end plate portion 8 side of the speed reducer 1 so as to cover the end plate portion 8 has been described. The case where the lubricant L is caused to flow into the accommodation portion 65 via the end plate side lubricant inflow hole 64 by the lubricant storage portion 74 formed by the housing 70 has been described. However, the present application is not limited thereto, and the housing 70 can also be omitted.

[0139] In this case, the lubricant L can also be injected directly from the end plate side lubricant inflow hole 64. The lubricant L can also be injected directly from the substrate side lubricant inflow hole 63. In the case where the lubricant L is injected directly from the substrate side lubricant inflow hole 63, the end plate side lubricant inflow hole 64 functions as an air discharge portion when the lubricant L flows into the accommodation portion 65.

[0140] In the case where the housing 70 is not provided, either of the substrate side lubricant inflow hole 63 and the end plate side lubricant inflow hole 64 can be formed alone. Even in the case of such a configuration, the lubricant L can be caused to easily flow into the accommodation portion 65 via the substrate side lubricant inflow hole 63 or the end plate side lubricant inflow hole 64.

[0141] In the embodiments disclosed in the present specification, a member composed of a plurality of objects can be integrated as the plurality of objects, and conversely, a member composed of one object can be divided into a plurality of objects. Whether or not integrated, it is only necessary to be configured in a manner that the object of the present invention can be achieved.

Claims

1. A rotating device, comprising: a first rotating body that is cylindrical; a pair of rolling bearings that are provided on the first rotating body; a second rotating body that is disposed on an inner side in a radial direction of the first rotating body; and a mechanism portion that is disposed on an inner side in a radial direction of the second rotating body, the pair of rolling bearings are disposed on both sides in an axial direction of the first rotating body, the second rotating body is rotatably supported on the first rotating body by the rolling bearings, the rotating device has: an accommodation portion that is formed between the first rotating body and the second rotating body; and a hole portion that communicates with an outside of the second rotating body and the accommodation portion, the accommodation portion accommodates the mechanism portion, the hole portion is disposed on the second rotating body, the rolling bearing has: an outer ring that is disposed on the first rotating body side; an inner ring that is disposed on the second rotating body side; a plurality of rolling elements that are disposed between the outer ring and the inner ring; and a retainer that is disposed between the outer ring and the inner ring, the retainer holds the plurality of rolling elements, a minimum opening width in an opening width of the hole portion that is orthogonal to a direction in which the hole portion extends is larger than a width between the outer ring and the retainer and a width between the inner ring and the retainer.

2. The rotating device according to claim 1, wherein the rotating device includes another mechanism portion that is provided on an outside of the second rotating body, the other mechanism portion transmits power to the mechanism portion, and the hole portion is disposed at a position that is exposed from the other mechanism portion, as viewed in an axial direction.

3. The rotating device according to claim 1 or 2, wherein the second rotating body has a first wall portion and a second wall portion that are opposed to each other on both sides in an axial direction with the accommodation portion interposed therebetween, the hole portion has: a first hole portion that is provided on the first wall portion; and a second hole portion that is provided on the second wall portion.

4. The rotating device according to claim 3, wherein the first hole portion is disposed at a position that is located on an inner side in a radial direction than the second hole portion.

5. The rotating device according to claim 4, wherein the rotating device has a plurality of the first hole portions and a plurality of the second hole portions, and the first hole portions and the second hole portions are respectively arranged in a circumferential direction with the rotation axis as a center.

6. The rotating device according to claim 2, wherein the rotating device includes a housing that covers the second rotating body, the rotating device has another accommodation portion that is formed by the housing and the second rotating body, the other mechanism portion is accommodated in the other accommodation portion, and the hole portion communicates with the other accommodation portion.

7. The rotating device according to claim 1, wherein the first rotating body has an inner tooth on an inner peripheral surface, the second rotating body has a first gear carrier and a second gear carrier that are opposed to each other in an axial direction, the mechanism portion includes: a crankshaft that is rotatably supported on the first gear carrier and the second gear carrier; and an external gear that is accommodated in the accommodation portion and is rotatably supported on the crankshaft, and is engaged with the inner tooth, and the hole portion is disposed in proximity to the inner tooth. ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ 8. The rotating device according to claim 7, wherein the hole portions have: a first hole portion provided in the first gear carrier; and a second hole portion provided in the second gear carrier, the first hole portion is disposed at a position radially inward of the second hole portion.

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