Locking mechanism, reduction gear, and geared motor

Abstract

The present invention provides a locking mechanism that enables smooth operation, as well as a reduction gear and geared motor equipped with such a locking mechanism. [Solution] The locking mechanism comprises a cylindrical case, a spring member disposed inside the case, an input body rotatable about a central axis relative to the case, an output body located on one axial side of the input body and rotatable about a central axis relative to the case, and a connecting portion that connects the input body and the output body with a gap in the circumferential direction. The input body has a recess. The output body has a protrusion that is inserted into the recess. The spring member is provided with a first claw portion and a second claw portion at both ends. The first claw portion and the second claw portion 72 are each positioned in the gap between the protrusion and the recess. The input body has a first opposing surface extending in the circumferential direction about a central axis. The output body has a second opposing surface facing the first opposing surface. At least one of the first opposing surface and the second opposing surface is provided with a lubricant-filling portion that is recessed so that lubricant can be filled into it.

Description

Technical Field

[0001] The present invention relates to a locking mechanism, a speed reduction device, and a geared motor.

Background Art

[0002] For a drive device that requires high torque, a geared motor in which a planetary gear mechanism as a speed reduction device is connected to a motor serving as a power source is adopted. Further, Patent Document 1 discloses a speed reduction mechanism with a brake that does not allow power transmission from the output shaft to the motor.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] When a locking mechanism is arranged in the power transmission path, friction occurs between members during the operation of the locking mechanism. When the friction increases, it becomes difficult for the locking mechanism to operate smoothly.

[0005] One aspect of the present invention is to provide a locking mechanism that enables smooth operation, as well as a speed reduction device and a geared motor provided with such a locking mechanism.

Means for Solving the Problems

[0006] A locking mechanism according to one aspect of the present invention includes a cylindrical case extending axially about a central axis, a spring member disposed inside the case and extending along the inner circumferential surface of the case, an input body rotatable about the central axis relative to the case, an output body located on one axial side of the input body and rotatable about the central axis relative to the case, and a connecting portion connecting the input body and the output body with a gap in the circumferential direction. The input body has a recess provided with a first inner surface facing one side in the circumferential direction and a second inner surface facing the other side in the circumferential direction. The output body has a convex portion provided with a first outer surface facing one side in the circumferential direction and a second outer surface facing the other side in the circumferential direction. A first claw portion and a second claw portion are provided at both ends of the spring member. The first claw portion faces the first inner surface and the second outer surface in the circumferential direction. The second claw portion faces the second inner surface and the first outer surface in the circumferential direction. The input body has a first opposing surface extending in the circumferential direction about the central axis. The output body has a second opposing surface facing the first opposing surface. At least one of the first opposing surface and the second opposing surface is provided with a lubricant-filling portion that is recessed so as to be filled with lubricant.

[0007] A reduction gear according to one aspect of the present invention comprises the above-described locking mechanism, a sun gear that rotates about the central axis, a plurality of planetary gears that mesh with the sun gear, and an internal gear that meshes with the planetary gears. The input body supports the plurality of planetary gears so that they can revolve and rotate around the central axis.

[0008] A geared motor according to one aspect of the present invention comprises a reduction gear and a motor unit connected to the reduction gear. [Effects of the Invention]

[0009] According to one aspect of the present invention, a locking mechanism that enables smooth operation, and a reduction gear and geared motor equipped with such a locking mechanism are provided. [Brief explanation of the drawing]

[0010] [Figure 1] Figure 1 is a cross-sectional view of a geared motor according to one embodiment. [Figure 2] Figure 2 is a cross-sectional view of a locking mechanism according to one embodiment. [Figure 3] Figure 3 is an exploded perspective view of a locking mechanism according to one embodiment. [Figure 4] Figure 4 is an exploded perspective view of a locking mechanism according to one embodiment. [Figure 5] Figure 5 shows the cross-sectional area of ​​the locking mechanism along the VV line in Figure 2. [Figure 6] Figure 6 is a schematic diagram showing the positional relationship between the spring member, the first flange portion, and the second flange portion of one embodiment. [Modes for carrying out the invention]

[0011] Hereinafter, a geared motor according to an embodiment of the present invention will be described with reference to the drawings. Note that the scope of the present invention is not limited to the following embodiments, and can be arbitrarily modified within the scope of the technical concept of the present invention.

[0012] The drawing shows the Z-axis parallel to the central axis J. In the following description, unless otherwise specified, the Z-axis direction will simply be referred to as the "axial direction," the +Z side as the "one axial side," and the -Z side as the "other axial side." Note that the vertical direction in this specification is a direction set for the convenience of explanation and does not limit the orientation when the geared motor is used. Furthermore, in the following description, the circumferential direction around the central axis J will simply be referred to as the "circumferential direction," and the radial direction relative to the central axis J will simply be referred to as the "radial direction."

[0013] The arrows θ shown in the diagrams indicate the circumferential direction. In the following explanation, the side pointed to by arrow θ (+θ side) will be referred to as "one side of the circumferential direction," and the side opposite to the direction pointed to by arrow θ (-θ side) will be referred to as "the other side of the circumferential direction."

[0014] <Geared Motor> FIG. 1 is a cross-sectional view of the geared motor 1. The geared motor 1 includes a motor unit 2 and a speed reduction device 3 connected to the motor unit 2. Hereinafter, each part of the geared motor 1 will be described in detail.

[0015] <Motor unit> The motor unit 2 has a motor shaft 22 that extends axially about the central axis J. The motor shaft 22 protrudes axially on one side (+Z) in the motor unit 2. The motor shaft 22 rotates around the central axis J. A first sun gear 33a is fixed to the end of the motor shaft 22 on one side (+Z) in the axial direction. The motor unit 2 is connected to the speed reduction device 3.

[0016] <Speed reduction device> The speed reduction device 3 is located on one side (+Z) in the axial direction of the motor unit 2. The speed reduction device 3 reduces the rotation output from the motor unit 2.

[0017] The speed reduction device 3 has a first planetary gear mechanism 30A, a second planetary gear mechanism 30B, and a third planetary gear mechanism 30C. The first planetary gear mechanism 30A, the second planetary gear mechanism 30B, and the third planetary gear mechanism 30C are arranged in this order from the other side (-Z) in the axial direction to the one side (+Z) in the axial direction. That is, the speed reduction device 3 has a plurality of planetary gear mechanisms 30A, 30B, 30C connected to each other along the axial direction. The power output from the motor unit 2 is transmitted in the order of the first planetary gear mechanism 30A, the second planetary gear mechanism 30B, and the third planetary gear mechanism 30C, and is output at the output shaft 36c of the third planetary gear mechanism 30C.

[0018] The speed reduction device 3 includes a cylindrical housing 40, a first sun gear 33a, three first planet gears 33b, a first internal gear 33c, a first carrier 31, a second sun gear (sun gear) 31c, three second planet gears (planet gears) 34b, a second internal gear (internal gear) 34c, a locking mechanism (second carrier) 9, a third sun gear 32c, three third planet gears 35b, a third internal gear 35c, and an output shaft 36c. In this embodiment, the first carrier 31 and the second sun gear 31c are parts of a single member.

[0019] The first sun gear 33a, the first planet gears 33b, the first carrier 31, and the first internal gear 33c constitute a first planetary gear mechanism 30A. The second sun gear 31c, the second planet gears 34b, the locking mechanism 9, and the second internal gear 34c constitute a second planetary gear mechanism 30B. The third sun gear 32c, the third planet gears 35b, the third carrier 36, and the third internal gear 35c constitute a third planetary gear mechanism 30C.

[0020] The housing 40 has a cylindrical portion 41 extending axially about a central axis J. On the inner peripheral surface 41a of the cylindrical portion 41, the first internal gear 33c, the third internal gear 35c, and the case 90 of the locking mechanism 9 are fixed. Also, the second internal gear 34c is fixed to the case 90. That is, the housing 40 restricts the rotation of the first internal gear 33c, the second internal gear 34c, and the third internal gear 35c about the central axis J. The first internal gear 33c, the second internal gear 34c, and the third internal gear 35c do not necessarily have to be fixed to the housing 40 as long as their relative rotation with respect to the housing 40 is restricted. Also, the first internal gear 33c, the second internal gear 34c, and the third internal gear 35c may be integrally formed with the housing 40.

[0021] The first sun gear 33a extends axially about the central axis J. The first sun gear 33a is fixed to the motor shaft 22 and rotates about the central axis J together with the motor shaft 22.

[0022] The first internal gear 33c is annular in shape with the central axis J at its center. The first internal gear 33c surrounds the first sun gear 33a from the radially outer side. A gap is provided between the first internal gear 33c and the first sun gear 33a for arranging the first planetary gear 33b. The first internal gear 33c meshes with the first planetary gear 33b.

[0023] The reduction gear 3 of this embodiment is provided with three first planetary gears 33b. The three first planetary gears 33b are arranged at equal intervals in the circumferential direction of the central axis J. In the radial direction, the three first planetary gears 33b are positioned between the first sun gear 33a and the first internal gear 33c. The three first planetary gears 33b mesh with the first sun gear 33a and the first internal gear 33c. The three first planetary gears 33b revolve around the central axis J as the first sun gear 33a rotates. A retaining hole is provided in the center of each first planetary gear 33b, opening to one side (+Z) in the axial direction.

[0024] The first carrier 31 has a first disc portion 31b and three first sub-shafts 31a. The first disc portion 31b is disc-shaped with respect to the central axis J. The first disc portion 31b is located on the other axial side (-Z) of the second planetary gear 34b and on one axial side (+Z) of the first planetary gear 33b. The first disc portion 31b is connected to the second sun gear 31c. The first disc portion 31b is located on one axial side (+Z) of the first sun gear 33a and the first planetary gear 33b. The three first sub-shafts 31a extend from the first disc portion 31b on the other axial side (-Z).

[0025] The first sub-shafts 31a are inserted into the holding holes of the first planetary gears 33b. Each of the three first sub-shafts 31a rotatably supports the first planetary gears 33b. That is, the first carrier 31 rotatably supports the multiple first planetary gears 33b from one axial side (+Z). The first carrier 31 rotates about the central axis J as the three first planetary gears 33b orbit and rotate. That is, the first carrier 31 rotatably supports the multiple first planetary gears 33b around the central axis J.

[0026] The second solar gear 31c protrudes from the first disc portion 31b in one axial direction (+Z). The second solar gear 31c extends from the first disc portion 31b in one axial direction (+Z) around the central axis J. The second solar gear 31c rotates together with the first carrier 31 around the central axis J in accordance with the orbital rotation of the first planetary gear 33b.

[0027] The second internal gear 34c is annular in shape with the central axis J at its center. The second internal gear 34c surrounds the second sun gear 31c from the radially outer side. A gap is provided between the second internal gear 34c and the second sun gear 31c for arranging the second planetary gear 34b. The second internal gear 34c meshes with the second planetary gear 34b.

[0028] The reduction gear 3 of this embodiment is provided with three second planetary gears 34b. The three second planetary gears 34b are arranged at equal intervals in the circumferential direction of the central axis J. In the radial direction, the three second planetary gears 34b are positioned between the second sun gear 31c and the second internal gear 34c. The three second planetary gears 34b mesh with the second sun gear 31c and the second internal gear 34c. The three second planetary gears 34b revolve and rotate in the circumferential direction of the central axis J as the second sun gear 31c rotates. A retaining hole is provided in the center of the second planetary gear 34b, opening to one side (+Z) in the axial direction.

[0029] The locking mechanism 9 comprises a case 90, a spring member 70, an input body 50, an output body 60, and a connecting portion 80. The locking mechanism 9 transmits power from the second planetary gear 34b in the input body 50 to the output body 60 via the connecting portion 80. The locking mechanism 9 also functions as a locking mechanism that restricts the transmission of torque from the output body 60 to the input body 50. The locking function of the locking mechanism 9 will be described in detail later.

[0030] The connecting portion 80 of the locking mechanism 9 has a shaft portion 81 fixed to the input body 50. The shaft portion 81 has a second sub-shaft portion 81b extending from the input body 50 to the other axial side (-Z). The second sub-shaft portion 81b is inserted into the holding hole of the second planetary gear 34b. The three second sub-shaft portions 81b each rotatably support the second planetary gear 34b. In other words, the locking mechanism 9 supports the multiple second planetary gears 34b so that they can revolve and rotate around the central axis J. In other words, the input body 50 rotatably supports the multiple second planetary gears 34b from one axial side (+Z). The input body 50 rotates about the central axis J in accordance with the revolving rotation of the three second planetary gears 34b. The third solar gear 32c is fixed to the output body 60.

[0031] The third sun gear 32c extends axially in one direction (+Z) around the central axis J. The third sun gear 32c is positioned inside the third internal gear 35c. The third sun gear 32c extends axially around the central axis J. The third sun gear 32c rotates around the central axis J in conjunction with the revolution of 32.

[0032] The third internal gear 35c is annular in shape with the central axis J at its center. The third internal gear 35c surrounds the third sun gear 32c from the radially outer side. A gap is provided between the third internal gear 35c and the third sun gear 32c for arranging the third planetary gear 35b. The third internal gear 35c meshes with the third planetary gear 35b.

[0033] The reduction gear 3 of this embodiment is provided with three third planetary gears 35b. The three third planetary gears 35b are arranged at equal intervals in the circumferential direction of the central axis J. In the radial direction, the three third planetary gears 35b are positioned between the third sun gear 32c and the third internal gear 35c. The three third planetary gears 35b mesh with the third sun gear 32c and the third internal gear 35c. The three third planetary gears 35b revolve and rotate in the circumferential direction of the central axis J as the third sun gear 32c rotates. A retaining hole is provided in the center of the third planetary gear 35b, opening to one side (+Z) in the axial direction.

[0034] The third carrier 36 has a third disc portion 36b and three third sub-shafts 36a. The third disc portion 36b is disc-shaped with a central axis J. The third disc portion 36b is located on one axial side (+Z) of the third sun gear 32c and the third planetary gear 35b. The three third sub-shafts 36a extend from the third disc portion 36b on the other axial side (-Z).

[0035] The third sub-shaft 36a is inserted into the holding hole of the third planetary gear 35b. Each of the three third sub-shafts 36a rotatably supports the third planetary gear 35b. That is, the third carrier 36 rotatably supports the multiple third planetary gears 35b from one axial side (+Z). The third carrier 36 rotates about the central axis J as the three third planetary gears 35b orbit and rotate. That is, the third carrier 36 rotatably supports the multiple third planetary gears 35b around the central axis J.

[0036] The output shaft 36c is fixed to the third carrier 36 and extends axially to one side (+Z) relative to the third carrier 36. The output shaft 36c is cylindrical with respect to the central axis J. The output shaft 36c protrudes axially to one side (+Z) from the axial end (+Z) of the housing 40. The output shaft 36c rotates together with the third carrier 36 about the central axis J as the third planetary gear 35b revolves.

[0037] <Locking mechanism> Next, the locking mechanism 9 will be described. The locking mechanism 9 is located inside the housing 40. The locking mechanism 9 receives the torque output from the motor unit 2 from the second planetary gear 34b and transmits it to the subsequent planetary gear mechanism 30C via the third sun gear 32c. On the other hand, the locking mechanism 9 receives the torque input from the output shaft 36c via the third sun gear 32c, but restricts its transmission to the second planetary gear 34b. This protects the motor unit 2 and restricts the free rotation of the output shaft 36c.

[0038] Figure 2 is a cross-sectional view of the locking mechanism 9. Figures 3 and 4 are exploded perspective views of the locking mechanism 9 viewed from different directions.

[0039] As shown in Figure 2, the locking mechanism 9 includes a case 90, an input body 50, an output body 60, a connecting part 80, and a spring member 70. Furthermore, as will be described later, the lubricant-filled part inside the locking mechanism 9 is filled with lubricant G. Lubricant G is, for example, lubricating grease. Alternatively, lubricant G may be lubricating oil soaked in a sponge or fibers held by the locking mechanism 9.

[0040] As shown in Figure 3, the case 90 has a cylindrical portion 91 and an inner projection 92. The cylindrical portion 91 is cylindrical in shape, extending axially with respect to the central axis J. The inner projection 92 protrudes radially inward from one end (+Z) on the axial side of the cylindrical portion 91. The inner projection 92 is plate-shaped, extending along a plane perpendicular to the axial direction. Furthermore, the inner projection 92 is annular in shape with respect to the central axis J.

[0041] As shown in Figure 1, the input body 50, output body 60, connecting part 80, and spring member 70 are housed inside the case 90. The case 90 is fixed, for example, to the inner circumferential surface 41a of the housing 40. In this way, the case 90 is fixed to the housing 40. On the other hand, the case 90 is not fixed to the input body 50, output body 60, connecting part 80, and spring member 70. Therefore, when the locking mechanism 9 transmits power, the input body 50, output body 60, connecting part 80, and spring member 70 rotate around the central axis J inside the case 90. That is, the input body 50, output body 60, connecting part 80, and spring member 70 are rotatable about the central axis J relative to the case 90.

[0042] As shown in Figure 3, the input body 50 has an input plate portion 51, a surrounding wall portion 52, and a first flange portion 56. In addition, a recess 53 is provided on the outer edge of the input body 50 that is recessed radially inward.

[0043] The recess 53 has a bottom surface 53c facing radially outward, a first inner surface 53a facing one side in the circumferential direction (+θ side), and a second inner surface 53b facing the other side in the circumferential direction (-θ side). The bottom surface 53c is arc-shaped with respect to the central axis J.

[0044] The input plate portion 51 is plate-shaped and extends along a plane perpendicular to the central axis J. When viewed from the axial direction, the input plate portion 51 is approximately circular with a portion where the recess 53 is provided missing. The input plate portion 51 has a first opposing surface 51f facing one side (+Z) in the axial direction. That is, the input body 50 has a first opposing surface 51f. The first opposing surface 51f extends in the circumferential direction centered on the central axis.

[0045] The first opposing surface 51f is provided with a circular recess (lubricant-filled portion) 54 that is recessed in the other axial direction (-Z). The circular recess 54 is circular with its center axis J. The circular recess 54 has an inner circumferential surface 54c facing radially inward and a bottom surface 54b facing one axial direction (+Z). As shown in Figure 2, the circular recess 54 is filled with lubricant G. That is, the circular recess 54 is recessed so that it can be filled with lubricant G.

[0046] As shown in Figure 3, the input plate portion 51 is provided with a plurality of support holes 51h (three in this embodiment) that penetrate in the axial direction. The plurality of support holes 51h are arranged at equal intervals along the circumferential direction. The shaft portion 81 of the connecting portion 80 is inserted into the support holes 51h. The shaft portion 81 is fixed, for example, to the support holes 51h.

[0047] The surrounding wall portion 52 extends from the outer edge of the input plate portion 51 in one axial direction (+Z). The surrounding wall portion 52 is substantially cylindrical, interrupted at the recess 53. At the end of the surrounding wall portion 52 on one axial direction (+Z), two end face recesses 52a are provided, recessed in the other axial direction (-Z) relative to the tip surface of the surrounding wall portion 52.

[0048] The first flange portion 56 extends radially outward from the end of the outer peripheral surface of the input plate portion 51 facing radially outward on the other axial side (-Z). The first flange portion 56 is substantially annular, interrupted at the recess 53. As shown in Figure 2, the first flange portion 56 is located on the other axial side (-Z) of the spring member 70. The surface of the first flange portion 56 facing one axial side (+Z) is axially opposite to the spring member 70.

[0049] As shown in Figure 3, the first flange portion 56 has a plate-shaped first flange portion body 56a extending along a plane perpendicular to the central axis J, and a projection 57 projecting from the first flange portion body 56a in one axial direction (+Z). The plate thickness of the first flange portion body 56a is sufficiently small compared to the plate thickness of the input plate portion 51. The projection 57 is located at the end of the first flange portion body 56a on one circumferential side (+θ). The first flange portion body 56a has a first surface 56f facing in one axial direction (+Z). The projection 57 also has a second surface 57f facing in one axial direction (+Z). Therefore, the surface of the first flange portion 56 facing in one axial direction (+Z) (i.e., the surface facing the spring member 70) is provided with the first surface 56f and the second surface 57f. The second face 57f is located one axial direction (+Z) relative to the first face 56f.

[0050] As shown in Figure 2, the output unit 60 is positioned inside the case 90. The output unit 60 is located on one axial side (+Z) of the input unit 50. The output unit 60 is rotatable about the central axis J relative to the case 90. The output unit 60 rotates together with the input unit 50 about the central axis J due to the torque transmitted from the input unit 50.

[0051] As shown in Figure 4, the output unit 60 has an output plate portion 61, a second flange portion 66, and a protrusion portion 63.

[0052] The output plate portion 61 is plate-shaped and extends along a plane perpendicular to the central axis J. The output plate portion 61 is inserted radially inward into the surrounding wall portion 52. A hole 61h is provided in the output plate portion 61. As shown in Figure 1, the third sun gear 32c is fixed to the hole 61h. As a result, the output body 60 rotates around the central axis J together with the third sun gear 32c.

[0053] As shown in Figure 4, the output plate portion 61 has a second opposing surface 61f facing the other axial direction (-Z). That is, the output body 60 has a second opposing surface 61f. The second opposing surface 61f extends in the circumferential direction centered on the central axis. The second opposing surface 61f faces the first opposing surface 51f.

[0054] The second opposing surface 61f is provided with a cylindrical portion 65 and a plurality (three in this embodiment) of groove portions (lubricant-filled portions) 64. The cylindrical portion 65 is cylindrical in shape with the central axis J as its center. A hole 61h opens at the tip surface 65a on the other axial side (-Z) of the cylindrical portion 65.

[0055] As shown in Figure 2, the cylindrical portion 65 is inserted into the circular recess 54. The diameter of the cylindrical portion 65 is smaller than the diameter of the circular recess 54. The outer circumferential surface 65c of the cylindrical portion 65 faces the inner circumferential surface 54c of the circular recess 54 with a small gap between them. This allows the output body 60 to be guided by the input body 50 so that it can rotate relative to the central axis J. The tip surface 65a of the cylindrical portion 65 faces the bottom surface 54b of the circular recess 54 with a gap GB between them. The lubricant G filling the circular recess 54 is held in the gap GB between the tip surface 65a of the cylindrical portion 65 and the bottom surface 54b of the circular recess 54. As the output body 60 and the input body 50 rotate relative to each other, the lubricant G in the circular recess 54 flows through the small gap between the outer circumferential surface 65c of the cylindrical portion 65 and the inner circumferential surface 54c of the circular recess 54 and into the space between the first opposing surface 51f and the second opposing surface 61f.

[0056] As shown in Figure 4, the multiple grooves 64 are arranged at equal intervals in the circumferential direction. The grooves 64 also extend along the circumferential direction. As shown in Figure 2, the grooves 64 are filled with lubricant G. That is, the grooves 64 are recessed to allow for the filling of lubricant G. As the output body 60 and the input body 50 rotate relative to each other, the lubricant G in the grooves 64 flows between the first opposing surface 51f and the second opposing surface 61f. As a result, the lubricant G reduces the sliding resistance between the first opposing surface 51f and the second opposing surface 61f.

[0057] Figure 5 shows the cross-sectional area of ​​the locking mechanism 9 along the VV line in Figure 2. As shown in Figure 5, the output plate portion 61 is provided with a plurality of openings 82 (three in this embodiment) that penetrate in the axial direction. The plurality of openings 82 are arranged at equal intervals in the circumferential direction. Each opening 82 opens in the axial direction and extends along the circumferential direction. In this embodiment, the openings 82 are notches provided on the outer edge of the output plate portion 61 and recessed radially inward. However, the openings 82 may be holes as long as they penetrate the output plate portion 61. The plurality of openings 82 are arranged at equal intervals along the circumferential direction. The shaft portion 81 of the connecting portion 80 is inserted into each opening 82.

[0058] As shown in Figure 4, the second flange portion 66 includes a plurality (three in this embodiment) of divided flange portions 66a, 66b, and 66c that are divided from each other in the circumferential direction. Hereafter, when distinguishing between the three divided flange portions 66a, 66b, and 66c, they will be referred to as the first divided flange portion 66a, the second divided flange portion 66b, and the third divided flange portion 66c, respectively.

[0059] The segmented flange portions 66a, 66b, and 66c each extend radially outward from one end on the axial side (+Z) of the outer peripheral surface of the output plate portion 61 that faces radially outward. The segmented flange portions 66a, 66b, and 66c are plate-shaped and extend along a plane perpendicular to the central axis J. The thickness of the segmented flange portions 66a, 66b, and 66c is sufficiently small compared to the thickness of the output plate portion 61.

[0060] As shown in Figure 5, the first split flange portion 66a is positioned within the recess 53 of the input body 50. The second split flange portion 66b and the third split flange portion 66c are positioned within different end face recesses 52a of the input body 50.

[0061] As shown in Figure 2, the second flange portion 66 is located on one axial side (+Z) of the spring member 70. The surface of the second flange portion 66 facing the other axial side (-Z) faces the spring member 70 in the axial direction. The surface of the second flange portion 66 facing one axial side (+Z) faces the inner projection 92 of the case 90 in the axial direction.

[0062] As shown in Figure 3, the first split flange portion 66a has a third surface 66af facing the other axial direction (-Z). The second split flange portion 66b has a fourth surface 66bf facing the other axial direction (-Z). The fourth surface 66bf is located further to the other axial direction (-Z) than the third surface 66af. The third split flange portion 66c has a fifth surface 66cf facing the other axial direction (-Z). The fifth surface 66cf is located further to the other axial direction (-Z) than the third surface 66af and the fourth surface 66bf. In other words, the surface of the second flange portion 66 facing the other axial direction (-Z) (i.e., the surface facing the spring member 70) is provided with a third surface 66af, a fourth surface 66bf, and a fifth surface 66cf, which are located at different axial positions from each other.

[0063] As shown in Figure 4, the protrusion 63 projects in the other axial direction (-Z) from the surface of the first divided flange portion 66a facing the other axial direction (-Z). The protrusion 63 is positioned within the recess 53. The protrusion 63 has a first outer surface (63a) facing one circumferential direction (+θ side) and a second outer surface 63b facing the other circumferential direction (-θ side).

[0064] As shown in Figure 5, the first inner surface 53a of the recess 53 and the second outer surface 63b of the protrusion 63 are positioned opposite each other with a gap in between. Also, when viewed from the axial direction, the second inner surface 53b of the recess 53 is positioned opposite the first outer surface 63a of the protrusion 63 with a gap in between.

[0065] The connecting portion 80 connects the input body 50 and the output body 60 with a gap in the circumferential direction. The rotation of the input body 50 is absorbed by the circumferential gap of the connecting portion 80 and then transmitted to the output body 60. The locking mechanism 9 has a plurality of (three in this embodiment) connecting portions 80. The plurality of connecting portions 80 are arranged at equal intervals along the circumferential direction. Each connecting portion 80 has a shaft portion 81 fixed to the input plate portion 51 and an opening 82 provided in the output plate portion 61. The shaft portion 81 is inserted into the opening 82.

[0066] The shaft portion 81 is cylindrical. The length dimension H along the circumferential direction of the opening 82 is greater than the diameter D of the shaft portion 81. Therefore, a circumferential gap GA is provided between the outer circumference of the shaft portion 81 and the inner surface of the opening 82. The circumferential length dimension of the gap GA between the shaft portion 81 and the opening 82 is the difference (HD) between the length dimension H along the circumferential direction of the opening 82 and the diameter D of the shaft portion 81. The shaft portion 81 is movable circumferentially within the opening 82 within the range of the gap GA. When the input body 50 rotates about the central axis J, the shaft portion 81 absorbs the circumferential gap within the opening 82 and then contacts the inner surface of the opening 82. After contacting the inner surface of the opening 82, the shaft portion 81 transmits the torque of the input body 50 to the output body 60.

[0067] As shown in Figure 4, the spring member 70 is a coil spring that extends spirally around the central axis J. Note that the configuration of the spring member 70 is not limited to this embodiment. The spring member 70 may also be a plate-shaped spring.

[0068] As shown in Figure 2, the spring member 70 is positioned in the axial direction between the first flange portion 56 and the second flange portion 66. The spring member 70 is also positioned inside the case 90 and extends along the inner circumferential surface 91a of the case 90.

[0069] The spring member 70 is positioned inside the case 90 with an initial compression applied in a direction that reduces its inner diameter. Therefore, the outer circumferential surface of the spring member 70 in its initial state is in contact with the inner circumferential surface 91a of the case 90. Also, the inner circumferential surface of the spring member 70 in its initial state faces the input body 50 and the output body 60 with a radial gap between them.

[0070] As shown in Figure 5, the spring member 70 has a helical portion 73 that extends spirally with the central axis J as its approximate center, a first claw portion 71 connected to one end of the helical portion 73, and a second claw portion 72 connected to the other end of the helical portion 73. That is, the first claw portion 71 and the second claw portion 72 are provided at both ends of the spring member 70. The first claw portion 71 and the second claw portion 72 protrude radially inward from their respective ends of the helical portion 73. The helical portion 73 surrounds the input plate portion 51 and the output plate portion 61 from the radial outside.

[0071] The first claw portion 71 is positioned between the first inner surface 53a and the second outer surface 63b. Therefore, the first claw portion 71 faces the first inner surface 53a and the second outer surface 63b in the circumferential direction. The second claw portion 72 is positioned between the second inner surface 53b and the first outer surface 63a. Therefore, the second claw portion 72 faces the second inner surface 53b and the first outer surface 63a in the circumferential direction.

[0072] (Power transmission from input to output) When the input body 50 rotates around the central axis J in one direction (+θ) in the circumferential direction, the multiple shaft portions 81 move circumferentially around the central axis J along with the input body 50. The shaft portions 81 move circumferentially inside the opening 82 of the output body 60 until they contact the region of the inner surface of the opening 82 that faces the other direction (-θ) in the circumferential direction. When the shaft portions 81 contact the inner surface of the opening 82, the rotation of the input body 50 is transmitted to the output body 60, and the input body 50 and the output body 60 rotate together around the central axis J.

[0073] As the input body 50 rotates circumferentially in one direction (+θ) around the central axis J, the shaft portion 81 contacts the inner surface of the opening 82, and the first inner surface 53a of the recess 53 contacts the first claw portion 71 of the spring member 70. Furthermore, the input body 50 displaces the first claw portion 71 circumferentially in one direction (+θ) by the first inner surface 53a of the recess 53, compressing the helical portion 73 of the spring member 70 and reducing the outer diameter of the helical portion 73. As a result, a part of the helical portion 73 separates from the inner circumferential surface 91a of the case 90. The compression of the spring member 70 reduces the static and kinetic friction between the spring member 70 and the inner circumferential surface 91a of the case 90. As a result, the spring member 70 rotates together with the input body 50 around the central axis J while sliding against the inner circumferential surface 91a of the case 90 with little sliding resistance. According to this embodiment, when the locking mechanism 9 transmits power from the input body 50 to the output body 60, the spring member 70 is compressed, which reduces the energy loss associated with the sliding of the spring member 70 and improves the power transmission efficiency of the locking mechanism 9.

[0074] Although this explanation describes the case where the input body 50 rotates in one direction (+θ) in the circumferential direction, the locking mechanism 9 operates similarly even when the input body 50 rotates in the other direction (-θ) in the circumferential direction.

[0075] (Restriction of power transmission from output to input) When the output unit 60 attempts to rotate around the central axis J in one circumferential direction (+θ), the first outer surface 63a of the protrusion 63 displaces the first claw portion 71 of the spring member 70 in one circumferential direction (+θ), expanding the helical portion 73 of the spring member 70 radially outward and pressing the outer surface of the helical portion 73 against the inner circumferential surface 91a of the case 90. As the spring member 70 expands, the static friction force between the spring member 70 and the inner circumferential surface 91a of the case 90 increases, restricting the rotation of the spring member 70 relative to the case 90. Furthermore, as the rotation of the spring member 70 is restricted, the rotation of the output unit 60 is restricted by interference between the protrusion 63 and the first claw portion 71 of the spring member 70. As a result, the locking mechanism 9 restricts the transmission of power from the output unit 60 to the input unit 50.

[0076] Furthermore, when attempting to rotate the output body 60 in one circumferential direction (+θ), the first outer surface 63a of the protrusion 63 contacts the second claw portion 72 of the spring member 70 before the shaft portion 81 contacts the inner surface of the opening 82. As a result, the locking mechanism 9 can press the spring member 70 against the inner circumferential surface 91a of the case 90 and lock it before the input body 50 and the output body 60 begin to rotate synchronously. This limits the rotation of the output body 60 and suppresses the transmission of torque from the output body 60 to the input body 50.

[0077] Although this explanation describes the case where the output unit 60 rotates in one direction (+θ) in the circumferential direction, the locking mechanism 9 operates similarly even when the output unit 60 rotates in the other direction (-θ) in the circumferential direction.

[0078] (summary) According to this embodiment, the torque applied from the input body 50 is transmitted between the shaft portion 81 of the connecting portion 80 and the inner surface of the opening 82. On the other hand, the torque applied from the output body 60 is transmitted from the protrusion 63 to the spring member 70, locking it and limiting its transmission to the input body 50. In other words, with the locking mechanism 9 of this embodiment, the power transmission path and the part that performs the locking function are provided in different parts. Therefore, the concentration of load in one part of the locking mechanism 9 can be suppressed, and by miniaturizing each part, the locking mechanism 9 can be made smaller. As a result, the reduction gear 3 can be made smaller.

[0079] The connecting portion 80 of this embodiment consists of a shaft portion 81 fixed to the input body 50 and an opening 82 provided in the output body 60. According to this embodiment, the connecting portion 80 has a simple structure, is easy to assemble, and can transmit a large torque from the input body 50 to the output body 60.

[0080] In this embodiment, the case in which the opening 82 is provided in the output plate portion 61 and the shaft portion 81 is fixed to the input plate portion 51 has been described. However, the opening 82 may be provided in the input plate portion 51 and the shaft portion 81 may be fixed to the output plate portion 61. That is, the opening 82 may be provided in one of the input plate portion 51 and the output plate portion 61, and the shaft portion 81 may be fixed to the other of the input plate portion 51 and the output plate portion 61. Furthermore, the configuration of the connecting portion 80 is not necessarily limited to this embodiment, as long as it connects the input body 50 and the output body with a gap in the circumferential direction.

[0081] In this embodiment, multiple connecting portions 80 are provided along the circumferential direction. According to this embodiment, the stress applied to each connecting portion 80 during the power transmission process from the input body 50 to the output body 60 can be reduced, and by miniaturizing each connecting portion 80, the locking mechanism 9 can be miniaturized.

[0082] As shown in Figure 1, according to this embodiment, the shaft portion 81 is fixed to the input plate portion 51 and inserted into the opening 82 on one axial side (+Z) of the input plate portion 51. The shaft portion 81 also rotatably supports the second planetary gear 34b on the other axial side (-Z) of the input plate portion 51. In other words, the shaft portion 81 in this embodiment acts as a connecting portion 80 and plays a part in the power transmission from the input body 50 to the output body 60. Furthermore, the shaft portion 81 acts as a second sub-shaft portion 81b and plays a part in the power transmission from the second planetary gear 34b to the input body 50. In this way, the torque transmitted from the second planetary gear 34b is transmitted to the output body 60 by the shaft portion 81. Therefore, the load on the input body 50 during the power transmission process can be reduced, and the input body 50 can be made smaller. Furthermore, when adopting such a structure, by using a high-strength material (e.g., a metal material) as the material constituting the shaft portion 81, a lightweight material (e.g., a resin material) can be used for the input body 50. As a result, the weight of the reduction gear 3 can be reduced.

[0083] According to this embodiment, the input body 50 has a first opposing surface 51f, and the output body 60 has a second opposing surface 61f facing the first opposing surface 51f. The first opposing surface 51f is provided with a circular recess 54 filled with lubricant G. The second opposing surface 61f is provided with a groove 64 filled with lubricant G. As a result, the lubricant G in the circular recess 54 and the groove 64 flows between the first opposing surface 51f and the second opposing surface 61f, thereby reducing the sliding resistance acting between the first opposing surface 51f and the second opposing surface 61f. When the locking mechanism 9 is activated, the input body 50 and the output body 60 rotate relative to each other by the gap GA of the connecting portion 80. According to this embodiment, smooth relative rotation between the input body 50 and the output body 60 is possible, and power transmission and locking by the locking mechanism 9 can be performed smoothly.

[0084] In this embodiment, the case in which lubricant-filled portions (circular recesses 54 or grooves 64) are provided on both the first opposing surface 51f and the second opposing surface 61f has been described. However, if the lubricant-filled portions (circular recesses 54 or grooves 64) are provided on at least one of the first opposing surface 51f and the second opposing surface 61f, a certain level of effect in supplying lubricant G between the first opposing surface 51f and the second opposing surface 61f can be obtained.

[0085] Furthermore, in this embodiment, the case in which the first opposing surface 51f and the second opposing surface 61f face each other in the axial direction has been described. However, the first opposing surface 51f and the second opposing surface 61f only need to face each other, extend in the circumferential direction with respect to the central axis J, and face each other. That is, the first opposing surface 51f and the second opposing surface 61f only need to be surfaces that rub against each other due to the relative rotation of the input body 50 and the output body 60. For example, the first opposing surface 51f and the second opposing surface 61f may each be cylindrical surfaces extending along the circumferential direction and facing each other in the radial direction.

[0086] In this embodiment, the groove 64 extends in the circumferential direction and is aligned with the opening 82 in the circumferential direction. In this embodiment, the groove 64 is greater than the circumferential movable distance of the shaft 81 within the opening 82. Here, the circumferential movable distance of the shaft 81 within the opening 82 is the circumferential length dimension of the gap GA between the shaft 81 and the opening 82. The circumferential length dimension of the gap GA is expressed as the difference (HD) between the circumferential length dimension H of the opening 82 and the diameter D of the shaft 81. That is, according to this embodiment, the following equation holds. d>HD

[0087] The lubricant G filling the groove 64 adheres to the first opposing surface 51f covering the groove 64. Furthermore, the lubricant G flows between the first opposing surface 51f and the second opposing surface 61f due to the relative rotation of the input body 50 and the output body 60. According to this embodiment, the distance between the groove 64 and the opening 82 (i.e., dimension d) is greater than the relative range of motion between the input body 50 and the output body 60. Therefore, it is possible to suppress the lubricant G in the groove 64 from entering the opening 82 due to the relative rotation of the input body 50 and the output body 60. As a result, it is possible to suppress the lubricant G between the first opposing surface 51f and the second opposing surface 61f from separating from the first opposing surface 51f and the second opposing surface 61f through the opening 82, and the effect of the lubricant G can be sustained for a longer period of time.

[0088] Furthermore, the groove 64 and the opening 82 may have chamfered edges. In this case, the circumferential length dimension H of the opening 82 and the circumferential length dimension d between the groove 64 and the opening 82 do not include the chamfered portion.

[0089] In this embodiment, one of the first opposing surface 51f and the second opposing surface 61f (the second opposing surface 61f in this embodiment) is provided with a plurality of grooves 64 that serve as lubricant-filled sections. The plurality of grooves 64 are arranged in the circumferential direction. According to this embodiment, the lubricant G can be spread throughout the entire circumferential area between the first opposing surface 51f and the second opposing surface 61f by utilizing the relative rotation of the input body 50 and the output body 60. This makes it easier for the input body 50 and the output body 60 to rotate relative to each other smoothly.

[0090] As shown in Figure 2, in this embodiment, a circular recess 54 is provided on one of the first opposing surface 51f and the second opposing surface 61f (the first opposing surface 51f in this embodiment) as a lubricant-filled portion. A cylindrical portion 65 is provided on the other of the first opposing surface 51f and the second opposing surface 61f (the second opposing surface 61f in this embodiment). The circular recess 54 and the cylindrical portion 65 are both circular with a central axis J. The cylindrical portion 65 is inserted into the circular recess 54. As a result, the output body 60 is guided by the input body 50 so that it can rotate relative to the central axis J. The lubricant G in the circular recess 54 gradually flows between the first opposing surface 51f and the second opposing surface 61f through the gap between the outer circumferential surface 65c of the cylindrical portion 65 and the inner circumferential surface 54c of the circular recess 54 as the output body 60 and the input body 50 rotate relative to each other. According to this embodiment, lubricant G can be slowly supplied between the first opposing surface 51f and the second opposing surface 61f over a long period of time, and the sliding resistance between the first opposing surface 51f and the second opposing surface 61f can be reduced over a long period of time.

[0091] As shown in Figure 2, in this embodiment, the input body 50 has a first flange portion 56 located on the other axial side (-Z) of the spring member 70. The output body 60 has a second flange portion 66 located on one axial side (+Z) of the spring member 70. When the locking mechanism 9 transmits power from the input body 50 to the output body 60, the input body 50, the output body 60, and the spring member 70 rotate integrally around the central axis J. Therefore, the first flange portion 56 and the second flange portion 66 rotate integrally with the spring member 70.

[0092] If the axial end (+Z) of the spring member 70 comes into contact with another member located on the axial side (+Z) of the spring member 70 (for example, the second internal gear 34c shown in Figure 1), the spring member 70 will rub against the other member and wear down when the locking mechanism 9 transmits power. Similarly, if the axial end (+Z) of the spring member 70 comes into contact with another member located on the axial side (+Z) of the spring member 70 (for example, the inner projection 92 of the case 90), the spring member 70 will rub against the other member and wear down when the locking mechanism 9 transmits power. When the spring member 70 wears down, the linearity of the spring member 70 changes at the worn portion, and the original spring characteristics of the spring member 70 cannot be obtained. Furthermore, the spring member 70 of this embodiment has a first claw portion 71 at the axial end (+Z) and a second claw portion 72 at the axial end (-Z). Therefore, as wear progresses on one or the other axial end of the spring member 70, the first claw portion 71 and the second claw portion 72 become thinner, and there is a risk that the first claw portion 71 and the second claw portion 72 may be damaged when force is applied.

[0093] According to this embodiment, the first flange portion 56 of the input body 50 and the second flange portion 66 of the output body 60 protect the spring member 70 and suppress wear of the spring member 70. Therefore, changes in the spring characteristics of the spring member 70 due to wear can be suppressed. Furthermore, according to this embodiment, damage to the first claw portion 71 and the second claw portion 72 of the spring member 70 can be suppressed.

[0094] In this embodiment, the case in which the input body 50 and the output body 60 each have flange portions (first flange portion 56 and second flange portion 66) has been described. However, if at least one of the input body 50 or the output body 60 has a flange portion that faces the spring member 70 in the axial direction, the effect of suppressing wear of the spring member 70 can be obtained on at least this one side.

[0095] Figure 6 is a schematic diagram showing the positional relationship between the first flange portion 56 and the second flange portion 66 with respect to the helical portion 73 of the spring member 70. In Figure 6, the circumferential direction θ is shown as a straight line. As shown in Figure 6, the helical portion 73 extends with an inclination toward one side in the axial direction (+Z) as it moves toward one side in the circumferential direction (+θ).

[0096] The second surface 57f of the first flange portion 56 is located on one side (+θ) in the circumferential direction and one side (+Z) in the axial direction relative to the first surface 56f. According to this embodiment, the first surface 56f and the second surface 57f are positioned at different locations in the axial direction along the helical shape of the spring member 70. Therefore, the first flange portion 56 can support the spring member 70 from the other side (-Z) in the axial direction while maintaining the orientation of the spring member 70.

[0097] The third surface 66af, the fourth surface 66bf, and the fifth surface 66cf of the second flange portion 66 are arranged in this order as they move toward the other side in the circumferential direction (-θ). Furthermore, the third surface 66af, the fourth surface 66bf, and the fifth surface 66cf are arranged in this order toward the other side in the axial direction (-Z). According to this embodiment, the third surface 66af, the fourth surface 66bf, and the fifth surface 66cf are arranged at different positions in the axial direction along the helical shape of the spring member 70. Therefore, the second flange portion 66 can support the spring member 70 from one side in the axial direction (+Z) while maintaining the orientation of the spring member 70.

[0098] The reduction gear 3 of this embodiment has multiple planetary gear mechanisms 30A, 30B, and 30C, each having a sun gear, planetary gears, internal gears, and a carrier. Therefore, the reduction gear 3 can achieve a large reduction ratio.

[0099] Furthermore, the locking mechanism 9 of this embodiment functions as a carrier for one of the multiple planetary gear mechanisms 30A, 30B, and 30C (in this embodiment, the second planetary gear mechanism 30B). More specifically, the input body 50 of the locking mechanism 9 supports multiple second planetary gears 34b so that they can revolve and rotate around a central axis. According to this embodiment, by incorporating the locking mechanism 9 into a part of the second planetary gear mechanism 30B, the reduction gear 3 can be miniaturized.

[0100] The reduction gear 3 of this embodiment has three planetary gear mechanisms 30A, 30B, and 30C, and the locking mechanism 9 functions as the middle carrier (locking mechanism 9) among three carriers (third carrier 36, locking mechanism 9, first carrier 31) arranged along the axial direction. The power of the motor unit 2 is reduced in the order of the first planetary gear mechanism 30A, the second planetary gear mechanism 30B, and the third planetary gear mechanism 30C. Therefore, the locking mechanism 9 can be positioned at a point where torque and rotational speed are well balanced. As a result, it is possible to suppress excessive force being applied to the locking mechanism 9 while also suppressing the speed of the locking mechanism 9 from becoming too fast, thereby stabilizing the operation of the locking mechanism 9.

[0101] Although embodiments and modifications of the present invention have been described above, the configurations and combinations thereof in the embodiments are merely examples, and additions, omissions, substitutions, and other modifications are possible without departing from the spirit of the present invention. Furthermore, the present invention is not limited by the embodiments.

[0102] For example, in the embodiments described above, the internal gear is fixed and the power input from the sun gear is output from the carrier in the planetary gear mechanisms 30A, 30B, and 30C. However, in the planetary gear mechanism used in the reduction gear, the internal gear, sun gear, and carrier may rotate relative to each other, and the input may come from any of them and the output from any of them. For example, the carrier may be fixed and the power input from the sun gear may be output from the internal gear. Alternatively, the mechanism may have a speed change mechanism that switches the output part to change the reduction ratio.

[0103] Furthermore, this technology can be configured as follows: (A1) A cylindrical case extending axially with respect to the central axis, A spring member is disposed inside the case and extends along the inner circumferential surface of the case, An input body that can rotate about the central axis relative to the aforementioned case, An output body located on one axial side of the input body and rotatable about the central axis relative to the case, It has a connecting portion that connects the input body and the output body with a gap in the circumferential direction, The input body has a recess provided with a first inner surface facing one side in the circumferential direction and a second inner surface facing the other side in the circumferential direction. The output body has a protrusion provided with a first outer surface facing one side in the circumferential direction and a second outer surface facing the other side in the circumferential direction. The spring member is provided with a first claw portion and a second claw portion at both ends. The first claw portion faces the first inner surface and the second outer surface in the circumferential direction, The second claw portion faces the second inner surface and the first outer surface in the circumferential direction, The input body has a first opposing surface that extends in the circumferential direction with respect to the central axis, The output unit has a second opposing surface that faces the first opposing surface, A locking mechanism in which at least one of the first opposing surface and the second opposing surface is provided with a lubricant-filling portion that is recessed so as to be filled with lubricant. (A2) The connecting portion is An opening provided in one of the input body and the output body that opens in the axial direction and extends along the circumferential direction, It has a shaft portion that is fixed to the other of the input body and the output body and inserted into the opening, The lubricant filling section is provided on one of the input body and the output body, extends in the circumferential direction, and is aligned with the opening in the circumferential direction. The locking mechanism according to (A1), wherein the circumferential length between the lubricant-filled portion and the opening is greater than the circumferential length of the gap between the shaft portion and the opening. (A3) A plurality of lubricant-filled portions are provided on one of the first opposing surface and the second opposing surface, The multiple lubricant-filled portions are arranged in the circumferential direction, and the locking mechanism is as described in (A1) or (A2). (A4) The first opposing surface and the second opposing surface are surfaces facing opposite directions in the axial direction, A circular lubricant-filled portion centered on the central axis is provided on one of the first opposing surface and the second opposing surface. A locking mechanism according to any one of (A1) to (A3), wherein a cylindrical portion is provided on the other of the first opposing surface and the second opposing surface, which is inserted into the lubricant-filled portion. (A5) The locking mechanism described in any one of (A1) to (A4), A sun gear that rotates about the aforementioned central axis, Multiple planetary gears that mesh with the aforementioned sun gear, The planetary gear is equipped with an internal gear that meshes with the planetary gear, The input body is a reduction gear that supports a plurality of planetary gears so that they can revolve and rotate around the central axis. A reduction gear described in either item (A6) or (A5), A geared motor having a motor section connected to the aforementioned reduction gear.

[0104] Furthermore, this technology can be configured as follows: (B1) A cylindrical case extending axially with respect to the central axis, A spring member is disposed inside the case and extends along the inner circumferential surface of the case, An input body that can rotate about the central axis relative to the aforementioned case, An output body located on one axial side of the input body and rotatable about the central axis relative to the case, It has a connecting portion that connects the input body and the output body with a gap in the circumferential direction, The input body has a recess provided with a first inner surface facing one side in the circumferential direction and a second inner surface facing the other side in the circumferential direction. The output body has a protrusion provided with a first outer surface facing one side in the circumferential direction and a second outer surface facing the other side in the circumferential direction. The spring member is provided with a first claw portion and a second claw portion at both ends. The first claw portion faces the first inner surface and the second outer surface in the circumferential direction, The second claw portion faces the second inner surface and the first outer surface in the circumferential direction, A locking mechanism wherein at least one of the input body or the output body has a flange portion that faces the spring member in the axial direction. (B2) The input body has a first flange portion located on the other axial side of the spring member as the flange portion, The locking mechanism according to (B1), wherein the output body has a second flange portion located on one axial side of the spring member as the flange portion. (B3) The flange portion includes a plurality of divided flange portions that are divided from each other in the circumferential direction, The spring member is a coil spring that extends spirally around the central axis, The locking mechanism according to (B1) or (B2), wherein the surfaces of the multiple divided flange portions facing the spring member are arranged at different positions in the axial direction along the helical shape of the spring member. (B4) The spring member is a coil spring that extends spirally around the central axis, The locking mechanism according to any one of (B1) to (B3), wherein the surface of the flange portion facing the spring member is provided with a first surface and a second surface that are positioned at different axial positions along the helical shape of the spring member. (B5) The locking mechanism described in any one of the items (B1) to (B4), A sun gear that rotates about the aforementioned central axis, Multiple planetary gears that mesh with the aforementioned sun gear, The planetary gear is equipped with an internal gear that meshes with the planetary gear, The input body is a reduction gear that supports a plurality of planetary gears so that they can revolve and rotate around the central axis. (B6) The reduction gear described in (B5), A geared motor having a motor section connected to the aforementioned reduction gear. [Explanation of symbols]

[0105] 1...Geared motor, 2...Motor section, 3...Reduction device, 9...Locking mechanism, 31c...Second sun gear (sun gear), 34b...Second planetary gear (planetary gear), 34c...Second internal gear (internal gear), 50...Input body, 51f...First opposing surface, 53...Recess, 53a...First inner surface, 53b...Second inner surface, 54...Circular recess (lubricant filling section), 6 0…Output unit, 61f…Second opposing surface, 63…Convex part, 63a…First outer surface, 63b…Second outer surface, 64…Recessed groove (lubricant-filled part), 65…Cylindrical part, 70…Spring member, 71…First claw part, 72…Second claw part, 80…Connecting part, 81…Shaft part, 82…Opening, 90…Case, d,H…Length dimension, G…Lubricant, GA…Gap, J…Center axis

Claims

1. A cylindrical case extending axially with respect to the central axis, A spring member is disposed inside the case and extends along the inner circumferential surface of the case, An input body that can rotate about the central axis relative to the aforementioned case, An output body located on one axial side of the input body and rotatable about the central axis relative to the case, It has a connecting portion that connects the input body and the output body with a gap in the circumferential direction, The input body has a recess provided with a first inner surface facing one side in the circumferential direction and a second inner surface facing the other side in the circumferential direction. The output body has a protrusion provided with a first outer surface facing one side in the circumferential direction and a second outer surface facing the other side in the circumferential direction. The spring member is provided with a first claw portion and a second claw portion at both ends. The first claw portion faces the first inner surface and the second outer surface in the circumferential direction, The second claw portion faces the second inner surface and the first outer surface in the circumferential direction, The input body has a first opposing surface that extends in the circumferential direction with respect to the central axis, The output unit has a second opposing surface that faces the first opposing surface, At least one of the first opposing surface and the second opposing surface is provided with a lubricant-filling portion that is recessed so as to be filled with lubricant. Locking mechanism.

2. The aforementioned connecting portion is An opening provided in one of the input body and the output body that opens in the axial direction and extends along the circumferential direction, It has a shaft portion that is fixed to the other of the input body and the output body and inserted into the opening, The lubricant filling section is provided on one of the input body and the output body, extends in the circumferential direction, and is aligned with the opening in the circumferential direction. The circumferential length between the lubricant-filled portion and the opening is greater than the circumferential length of the gap between the shaft portion and the opening. The locking mechanism according to claim 1.

3. A plurality of lubricant-filled portions are provided on one of the first opposing surface and the second opposing surface. Multiple lubricant-filled sections are arranged in the circumferential direction. The locking mechanism according to claim 1.

4. The first opposing surface and the second opposing surface are surfaces facing opposite directions in the axial direction. A circular lubricant-filled portion centered on the central axis is provided on one of the first opposing surface and the second opposing surface. The other of the first opposing surface and the second opposing surface is provided with a cylindrical portion that is inserted into the lubricant-filled portion. The locking mechanism according to claim 1.

5. A locking mechanism according to any one of claims 1 to 4, A sun gear that rotates about the aforementioned central axis, Multiple planetary gears that mesh with the aforementioned sun gear, The planetary gear is equipped with an internal gear that meshes with the planetary gear, The input body supports a plurality of planetary gears so that they can revolve and rotate around the central axis. Reduction device.

6. The reduction gear according to claim 5, The motor unit connected to the reduction gear has Geared motor.

Images