JP2019113148A - Gear mechanism - Google Patents

Abstract

To obtain, for example, a gear mechanism having a new structure which enables further improvement of lubricity between a shaft and a gear.SOLUTION: A gear mechanism of the invention includes, for example, a first shaft provided with a lubrication oil storage part, having an infiltration passage in which at least one component of lubrication oil at least partially stored in the storage part seeps to an outer periphery, and formed by a porous metallic material, and a first gear which is supported by the first shaft in a manner that the first gear can rotate around the outer periphery.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a gear mechanism.

  2. Description of the Related Art A vehicle brake having a gear mechanism including a shaft and a gear rotatably supported by the shaft is conventionally known (for example, Patent Document 1).

JP, 2016-145030, A

  In this type of gear mechanism, if the lubricity between the shaft and the gear can be further enhanced, advantages such as improved durability can be obtained.

  Therefore, one of the problems of the present invention is, for example, to obtain a gear mechanism of a novel configuration capable of further improving the lubricity between the shaft and the gear.

  The gear mechanism of the present invention is, for example, a porous member provided with a housing portion for lubricating oil, and having an infiltration path through which at least a portion of the lubricating oil component at least a part is housed in the housing portion And a first gear rotatably supported on the first shaft so as to be rotatable about the outer periphery.

  According to the gear mechanism, for example, at least a part of the component of the lubricating oil contained in the containing portion can exude to the outer periphery via the infiltration path in the first shaft, and thus the exuded component Thus, the lubricity between the outer periphery and the inner periphery of the first gear can be enhanced.

  Further, the gear mechanism includes, for example, a support member connected to the first shaft and made of a metal material having a higher density than the porous metal material. According to such a configuration, for example, the rigidity and strength of the support member can be further increased, and the durability reliability of the support member, and hence the gear mechanism can be improved.

  The gear mechanism includes, for example, a first sun gear, a first ring gear, a plurality of first pinion gears as the first gear meshed with the first sun gear and the first ring gear, and the plurality of first pinion gears. A first planetary gear mechanism including: a first planetary carrier including a plurality of first pinion shafts as the first shaft supported thereon; According to such a configuration, for example, when the first planetary gear mechanism is used as a speed reduction mechanism, the wear condition becomes stricter (more prone to wear) than other parts, and the outer periphery of the first pinion shaft and the first pinion gear Wear due to sliding with the inner circumference can be suppressed.

  In addition, the gear mechanism includes, for example, a second sun gear, a second ring gear, a plurality of second pinion gears engaged with the second sun gear and the second ring gear, and a plurality of second pinion gears respectively supporting the plurality of second pinion gears. And a second planetary carrier including a two-pinion shaft, at least one of the second sun gear, the second ring gear, and the second planetary carrier being made of a synthetic resin material; A second planetary gear mechanism for transmitting the rotation to the planetary gear mechanism is provided. According to such a configuration, for example, at least a part of the components of the second planetary gear mechanism, which has a smaller torque than the first planetary gear mechanism and is less likely to wear than the first planetary gear mechanism, may be made of synthetic resin. Thus, the second planetary gear mechanism can be configured to be lighter.

  Further, in the gear mechanism, for example, an opening in which the first planetary gear mechanism and the second planetary gear mechanism overlap in the axial direction of the first pinion shaft and face the second planetary carrier of the housing portion. The end is covered by the second planetary carrier. According to such a configuration, for example, the lubricating oil contained in the housing portion is less likely to flow out from the open end, and the effect of enhancing the above-mentioned lubricity by the bleeding of the components of the lubricating oil is obtained for a longer period of time. be able to.

FIG. 1 is a schematic and exemplary cross-sectional view of a vehicle brake including the gear mechanism of the embodiment. FIG. 2 is a schematic and exemplary cross-sectional view of a portion of the caliper of the vehicle brake of the embodiment. FIG. 3 is an exemplary schematic cross-sectional view of a gear mechanism of a first modification. FIG. 4 is an exemplary schematic cross-sectional view of a gear mechanism of a second modified example.

  In the following, exemplary embodiments and variants of the invention are disclosed. The configurations of the embodiments and modifications shown below, and the operations and results (effects) provided by the configurations are examples. The present invention can also be realized by configurations other than those disclosed in the following embodiments and modifications. Further, according to the present invention, it is possible to obtain at least one of various effects (including derivative effects) obtained by the configuration.

  Moreover, the several gear mechanism of the following embodiment and modification is equipped with the same component. Therefore, according to the said several gear mechanism, the same effect based on the same component is acquired. In the following, those similar components are given the same or similar reference numerals, and the redundant description is omitted.

  Further, in the present specification, ordinal numbers are given for the sake of convenience in order to distinguish parts, parts, etc., and do not indicate priority or order.

[Embodiment]
FIG. 1 is a cross-sectional view of a brake 1 for a vehicle. As illustrated in FIG. 1, the brake 1 includes a motor 20, a rotation transmission mechanism 100, and a caliper 200 incorporating a rotary-to-linear motion conversion mechanism 50 (FIG. 2). The brake 1 can operate as a hydraulic brake and can also operate as an electric brake. The caliper 200 constitutes a hydraulic brake, and the motor 20, the rotation transmission mechanism 100, the rotary / linear motion conversion mechanism 50, and the caliper 200 constitute an electric brake. The electric brake is a so-called electric parking brake. That is, the brake 1 is configured such that the braking state by the electric brake function is maintained at the time of parking. However, the electric brake may operate at the time of traveling or at the time of temporary stop.

  The motor 20 and the rotation transmission mechanism 100 are housed in a housing 10. The housing 10 includes a casing 11, an inner cover 12 and an outer cover 13.

  The casing 11 is provided with a housing portion 11 a for housing the motor 20. The housing portion 11 a is a cylindrical hole with a bottom. The motor 20 is housed in the housing portion 11a in such a manner that one end 21a of the shaft 21 is exposed from the open end 11b of the housing portion 11a. The side surface (circumferential surface) and the bottom surface of the motor 20 are covered by the wall portion 11 c of the casing 11. The casing 11 is made of an insulating synthetic resin material.

  The motor 20 is covered by an inner cover 12 from the side opposite to the casing 11. The inner cover 12 covers the open end 11b of the housing portion 11a. The inner cover 12 is provided with a through hole 12a, and the shaft 21 of the motor 20 passes through the through hole 12a and is opposite to the motor 20 (body 20a), that is, the housing portion 11a of the inner cover 12 It is exposed to the other side. The inner cover 12 extends in a direction intersecting (orthogonal to) the rotation center Ax1. The inner cover 12 is coupled to the casing 11 by a coupling 14 such as a screw. The body 20 a of the motor 20 is covered by the casing 11 and the inner cover 12. The inner cover 12 is attached to the motor 20. The inner cover 12 is made of an insulating synthetic resin material. The inner cover 12 is an example of a motor bracket.

  The rotation transmission mechanism 100 includes an intermediate gear 41, a second planetary gear mechanism 42, and a first planetary gear mechanism 46. The rotation transmission mechanism 100 transmits the rotation of the shaft 21 of the motor 20 to the rotation / linear motion conversion mechanism 50 (FIG. 2). The rotation transmission mechanism 100 is an example of a speed reduction mechanism for braking. The rotation transmission mechanism 100 is not limited to the example of FIG. 1 and may be implemented as various configurations. The motor 20 is an example of a drive source.

  The intermediate gear 41 is rotatably provided around a rotation center Ax2 parallel to the rotation center Ax1, and has an input gear 41a and an output gear 41b. The input gear 41 a meshes with a pinion 22 fixed to the shaft 21 of the motor 20. The output gear 41 b drives the second planetary gear mechanism 42. The number of teeth of the output gear 41b is smaller than the number of teeth of the input gear 41a. Therefore, the rotation of the motor 20 is decelerated by the intermediate gear 41.

  The second planetary gear mechanism 42 has a second sun gear 43, a second planetary carrier 44, and a second ring gear 45.

  The second sun gear 43 and the second planetary carrier 44 rotate around a rotation center Ax3 parallel to the rotation centers Ax1 and Ax2. The second ring gear 45 is fixed to the casing 11. The center of the second ring gear 45 coincides with the rotation center Ax3.

  The second sun gear 43 has an input gear 43a and an output gear 43b. The input gear 43 a meshes with the output gear 41 b of the intermediate gear 41. The output gear 43 b drives the second planetary carrier 44. The second sun gear 43 is provided with a through hole centered on the rotation center Ax3, and a shaft 49 is press-fit into the through hole.

  The second planetary carrier 44 includes a second carrier base 44a, a plurality of second pinion shafts 44b integrally formed with the second carrier base 44a, and a plurality of rotatably supported by the second pinion shafts 44b. And the second pinion gear 44c. The second pinion gear 44c rotates about an axial center (rotation center) of the second pinion shaft 44b parallel to the rotation center Ax3. In the present embodiment, as an example, the number of second pinion shafts 44b is four, and the number of second pinion gears 44c is also four, but is not limited thereto.

  The second pinion gear 44c meshes with the output gear 43b of the second sun gear 43 radially inward of the rotation center Ax3, and meshes with the second ring gear 45 (inner teeth) radially outward of the rotation center Ax3. The second pinion gear 44c revolves around the second sun gear 43. The second carrier base 44a has a first sun gear 44d as an output unit. In such a configuration, the rotation of the intermediate gear 41 is decelerated by the second planetary gear mechanism 42 and output from the first sun gear 44 d.

  In the second planetary gear mechanism 42, a part of the second sun gear 43, the second carrier base 44a, the second pinion shaft 44b, and the second ring gear 45 are made of a synthetic resin material. On the other hand, the second pinion gear 44c is made of a metal material.

  The first planetary gear mechanism 46 has a first sun gear 44 d, a first planetary carrier 47, and a first ring gear 48.

  The first sun gear 44 d and the first planetary carrier 47 rotate around the rotation center Ax3. Also, the first ring gear 48 is fixed to the casing 11. The center of the first ring gear 48 coincides with the rotation center Ax3. The first sun gear 44d and the first planetary carrier 47 are rotatably supported by a shaft 49 fixed to the second sun gear 43 and extending along the rotation center Ax3.

  The first planetary carrier 47 includes a first carrier base 47a, a plurality of first pinion shafts 47b fixed to the first carrier base 47a, and a plurality of first pinion shafts 47b rotatably supported on the first pinion shaft 47b. And one pinion gear 47c. The first pinion gear 47c rotates about the axial center (rotation center) of the first pinion shaft 47b parallel to the rotation center Ax3. In the present embodiment, as an example, the number of first pinion shafts 47b is four, and the number of first pinion gears 47c is also four. However, the present invention is not limited to this.

  The first pinion gear 47c meshes with the first sun gear 44d radially inward of the rotation center Ax3, and meshes with the first ring gear 48 (inner teeth) radially outward of the rotation center Ax3. The first pinion gear 47c revolves around the first sun gear 44d. The first carrier base 47a has a projecting portion 47d as an output portion. The rotation of the second planetary gear mechanism 42 is decelerated by the first planetary gear mechanism 46 and output from the protrusion 47 d.

  In the first planetary gear mechanism 46, the first sun gear 44d, the first planetary carrier 47, and the first ring gear 48 are all made of, for example, a metallic material such as an iron-based material.

  The rotation member 51 (FIG. 2) of the rotary-to-linear motion conversion mechanism 50 is coupled to the protrusion 47 d of the first planetary gear mechanism 46 and rotates integrally with the protrusion 47 d. Thus, the rotating member 51 rotates in conjunction with the shaft 21 of the motor 20.

  In the present embodiment, the first pinion shaft 47b is provided with a bottomed cylindrical recess 47b1 extending along the rotation center thereof. The recess 47 b 1 is open to the second planetary gear mechanism 42 side. In other words, the open end 47b3 of the recess 47b1 is located at the end of the first pinion shaft 47b close to the second planetary gear mechanism 42. The open end 47b3 is covered with a gap at the disk-like base portion of the second carrier base 44a. The first pinion shaft 47 b is an example of a first shaft, the first pinion gear 47 c is an example of a first gear, and the first planetary carrier 47 is an example of a gear mechanism.

  Grease is accommodated in the recess 47b1. For example, grease is configured as a semisolid or semifluid by adding an additive such as a thickener to a base oil. The grease is an example of a lubricating oil, and the recess 47 b 1 is an example of a housing.

  The first pinion shaft 47b is made of, for example, a porous metal material such as a sintered material. The sintered material has an infiltration path which allows at least a part of the component of grease contained in the recess 47b1 to exude to the outer periphery 47b2. The infiltration path is formed by connecting a gap between the plurality of particles constituting the sintered material from the inner peripheral surface of the recess 47b1 to the outer periphery 47b2 of the first pinion shaft 47b. The specification of the infiltration path is the specification of the powder that constitutes the sintered material, depending on the usage period (guarantee period, life) of the first planetary gear mechanism 46, etc., as well as the selection of the grease component housed in the recess 47b1. It may be adjusted appropriately according to the method of construction, process parameters and the like.

  The first pinion shaft 47b is coupled to the first carrier base 47a by being press-fitted into a hole provided in the first carrier base 47a. The density of the first carrier base 47a is set higher than the density of the first pinion shaft 47b. The first carrier base 47a is an example of a support member.

  FIG. 2 is a cross-sectional view of the caliper 200. As shown in FIG. The caliper 200 has a body 201 and a piston 203. The body 201 is provided with a cylinder 202. The cylinder 202 is a bottomed cylindrical hole opened downward in FIG. 2 around the rotation center Ax3. The piston 203 is accommodated in the cylinder 202 so as to be capable of reciprocating along the rotation center Ax3. The cylinder 202 is provided with a fluid pressure chamber R. As the fluid pressure in the fluid pressure chamber R rises, the piston 203 pushes the back plate 205 a of the pad 205 downward in FIG. 2 and presses the lining 205 b against the disc D. As a result, a braking state by the hydraulic pressure brake is obtained in which the wheel (not shown) of the vehicle rotating integrally with the disc D is braked. Specifically, the piston 203 has an outer peripheral surface 203b in the form of a cylindrical outer surface, and an end surface 203c on the opposite side (downward in FIG. 2) to the fluid pressure chamber R. A minute gap (clearance) is set between the outer peripheral surface 203 b of the piston 203 and the inner peripheral surface 202 a of the cylinder 202, and the outer peripheral surface 203 b is in the inner peripheral in the lubricated state where the working fluid exists in the clearance. It slides with the surface 202a. The seal 62 is interposed between the outer circumferential surface 203 b and the inner circumferential surface 202 a, and suppresses the leakage of the hydraulic fluid from the fluid pressure chamber R via a gap. Further, the seal 62 retracts the piston 203 to the side of the fluid pressure chamber R (upper side in FIG. 2) by an elastic force as the fluid pressure in the fluid pressure chamber R drops, and retracts the end face 203c of the piston 203 have. That is, when the pressure on the back plate 205a of the piston 203 is released along with the drop in the fluid pressure of the fluid pressure chamber R, the pressure on the disc D of the lining 205b by the piston 203 is released. The brake release state due to Thus, the caliper 200 can operate as a hydraulic brake. The pad 205 is an example of a braking member.

  Further, in the caliper 200, a rotational linear motion conversion mechanism 50 is provided. The rotary-to-linear motion conversion mechanism 50 has a rotating member 51 and a linear moving member 52. The rotation member 51 includes a coupling portion 51a, a flange 51b, and a shaft 51c, and is supported by the body 201 so as to be rotatable around a rotation center Ax3. The coupling portion 51a is coupled to a projecting portion 47d as an output portion of the first planetary gear mechanism 46 (rotation transmission mechanism 100). A thrust bearing 61 is provided between the flange 51 b and the body 201 of the caliper 200. The shaft 51c protrudes from the flange 51b to the opposite side (downward in FIG. 2) to the coupling portion 51a. An external thread 51d is provided on the outer peripheral surface of the shaft 51c. The rotating member 51 is an example of a first rotating member.

  The linear moving member 52 has a cylindrical portion 52a and a protrusion 52b. The shape of the cylindrical part 52a is a cylindrical shape centering on rotation center Ax3. A female screw 52c is provided on the inner surface of the cylindrical portion 52a, and the female screw 52c and the male screw 51d of the rotating member 51 are engaged with each other. The protrusion 52b protrudes outward in the radial direction of the rotation center Ax3 from the cylindrical portion 52a.

  The rotary-to-linear motion conversion mechanism 50 is accommodated in a recess 203 a provided in the piston 203. The recess 203 a is open toward the fluid pressure chamber R side (upper side in FIG. 2). The linear movement member 52 is provided movably in the axial direction (vertical direction in FIG. 2) of the rotation center Ax3 in the recess 203a. The recess 203a is provided with a groove 203d extending in the axial direction of the rotation center Ax3. The protrusion 52b of the linear motion member 52 is accommodated in the groove 203d so as to be movable along the groove 203d. That is, the rotation preventing mechanism of the linear moving member 52 is configured by the side surface of the groove 203 d and the projection 52 b of the linear moving member 52. Further, in the present embodiment, the rotation of the piston 203 about the rotation center Ax3 is restricted by the friction between the piston 203 and the seal 62 or the pad 205.

  As described above, in the present embodiment, the male screw portion 51 d of the rotating member 51 and the female screw portion 52 c of the linear moving member 52 mesh with each other, and the rotation of the protrusion 52 b of the linear moving member 52 is limited by the groove 203 d of the piston 203. Therefore, in response to the rotation of the rotation member 51, the linear movement member 52 linearly moves in the axial direction of the rotation center Ax3. The one-way rotation of the rotating member 51 based on the rotation of the shaft 21 of the motor 20 (hereinafter referred to as normal rotation) moves the linear moving member 52 downward in FIG. 2, and the piston 203 shows the back plate 205a. When pressing downward on 2, the piston 203 presses the lining 205 b of the pad 205 against the disc D. Thereby, a braking state by the electric brake function is obtained in which the wheel (not shown) of the vehicle rotating integrally with the disc D is braked. On the other hand, when the linear moving member 52 moves upward in FIG. 2 by the reverse rotation of the rotating member 51 based on the reverse rotation of the shaft 21 of the motor 20 and the pressing of the piston 203 against the back plate 205a is released, The pressing of the lining 205b against the disc D by the wheel 203 is released, whereby a release state of braking by the electric brake function is obtained. Thus, the motor 20, the rotation transmission mechanism 100, the rotary-to-linear motion conversion mechanism 50, and the caliper 200 can operate as an electric brake.

  As described above, in the present embodiment, for example, the first pinion shaft 47 b (first shaft) is provided with the recess 47 b 1 (housing portion) for housing grease (lubricating oil), and the first pinion shaft 47 b is The at least one component of the grease contained in the recess 47b1 is made of a porous metal material having an infiltration path which exudes to the outer periphery 47b2. According to such a configuration, for example, a part of components such as base oil contained in the grease contained in the recess 47b1 may exude to the outer periphery 47b2 via the infiltration path in the first pinion shaft 47b. Therefore, the lubricity of the outer periphery 47b2 and the inner periphery 47c1 of the first pinion gear 47c can be enhanced by the exuded component. Therefore, for example, it is possible to suppress the acceleration of wear due to the sliding between the outer periphery 47b2 of the first pinion shaft 47b and the inner periphery 47c1 of the first pinion gear 47c, thereby suppressing the first planetary carrier 47 (gear mechanism). The endurance reliability of the first planetary gear mechanism 46, the rotation transmission mechanism 100, and the brake 1 can be enhanced, and their lifetime can be further lengthened.

  Further, in the present embodiment, for example, the first carrier base 47a (support member) to which the first pinion shaft 47b is coupled is made of a metal material having a higher density than the first pinion shaft 47b. According to such a configuration, for example, the rigidity and strength of the first carrier base 47a can be further increased, and the first planetary carrier 47, and hence the first planetary gear mechanism 46, the rotation transmission mechanism 100, and the brake 1 can be provided. Durability can be enhanced and their lifetime can be made longer.

  Moreover, in the present embodiment, for example, the first shaft provided with the recess 47b1 and the infiltration path in the inside is the first pinion shaft 47b of the first planetary gear mechanism 46, and the first shaft rotatable about the outer periphery of the shaft The gear is a first pinion gear 47c. According to such a configuration, for example, when the first planetary gear mechanism 46 is used as a speed reduction mechanism, the outer circumference 47b2 of the first pinion shaft 47b and the first pinion shaft 47b where the wear condition becomes stricter (is easy to wear) than other parts. It is possible to suppress wear due to sliding with the inner periphery 47c1 of the one pinion gear 47c.

  Further, in the present embodiment, for example, the second planetary gear mechanism 42 that transmits the rotation (torque) of the motor 20 to the first planetary gear mechanism 46 by being interposed between the motor 20 and the first planetary gear mechanism 46. At least one of the second sun gear 43, the second planetary carrier 44, and the second ring gear 45 is made of a synthetic resin material. According to such a configuration, for example, at least a part of the components of the second planetary gear mechanism 42 which is smaller in torque than the first planetary gear mechanism 46 and less likely to be worn than the first planetary gear mechanism 46 is made of synthetic resin material. By comprising, the said 2nd planetary gear mechanism 42 and by extension, the rotation transmission mechanism 100 and the brake 1 can be comprised more lightweight.

  Further, in the present embodiment, for example, the open end 47b3 of the recess 47b1 (housing portion) provided in the first pinion shaft 47b is covered by the second planetary carrier 44. According to such a configuration, for example, the grease (lubricating oil) contained in the recess 47b1 is less likely to drain away from the opening end 47b3, and the lubricity between the outer periphery 47b2 and the inner periphery 47c1 due to bleeding of grease components. Can be obtained over a longer period of time.

First Modification
FIG. 3 is an exemplary schematic cross-sectional view of a first planetary gear mechanism 46A including a first pinion shaft 47b and a first pinion gear 47c as a gear mechanism of the first modification. The first planetary gear mechanism 46A of the first modification may be provided instead of the first planetary gear mechanism 46 of the above embodiment. The first planetary gear mechanism 46A has the same components as the first planetary gear mechanism 46. However, in the first planetary gear mechanism 46A, the specifications of the recess 47b1 are different from those of the first planetary gear mechanism 46.

  As shown in FIG. 3, the first pinion shaft 47b protrudes from the first carrier base 47a to approach the second planetary gear mechanism 42 (upward in FIG. 3). The open end 47b3 of the recess 47b1 is provided at the end 47b4 of the first pinion shaft 47b close to the second planetary gear mechanism 42. The diameter of the recess 47b1 decreases as the first pinion shaft 47b approaches the root portion 47b5 which protrudes from the first carrier base 47a from the tip end 47b4 of the first pinion shaft 47b. That is, the shape of the concave portion 47b1 is a tapered shape that becomes thinner toward the root portion 47b5, and is in the shape of a mortar that spreads toward the opening end 47b3 (protruding end 47b4). In other words, the inner surface of the recess 47b1 has a conical inner surface.

  The stress generated in the first pinion shaft 47b during torque transmission often increases at the root portion 47b5. In this respect, according to the configuration as in this modification, for example, the cross-sectional area of the root portion 47b5 where the stress is increased in the first pinion shaft 47b (first shaft) is the cross section of the projecting end 47b4 provided with the open end 47b3 Since the area is larger than the area, rigidity and strength at the root portion 47b5 can be further increased. Therefore, for example, the rigidity and strength of the first pinion shaft 47b can be further increased, and the durability reliability of the first planetary carrier 47 and hence the first planetary gear mechanism 46A, the rotation transmission mechanism 100, and the brake 1 can be improved. And their lifetime can be made longer.

  Further, the bottom 47b6 of the recess 47b1 is located closer to the open end 47b3 (protruding end 47b4) than the root portion 47b5. According to such a configuration, the rigidity and strength of the first pinion shaft 47b at the root portion 47b5 can be further enhanced. The axial arrangement of the bottom portion 47b6 and the root portion 47b5 is the same as in the above embodiment and the following second modification.

Second Modified Example
FIG. 4 is an exemplary schematic cross-sectional view of a first planetary gear mechanism 46B including a first pinion shaft 47b and a first pinion gear 47c as a gear mechanism of the second modification. The first planetary gear mechanism 46B of the second modification may be provided instead of the first planetary gear mechanism 46 of the above embodiment. The first planetary gear mechanism 46 B has the same components as the first planetary gear mechanism 46. However, in the first planetary gear mechanism 46 B, the specifications of the first carrier base 47 a are different from those of the first planetary gear mechanism 46.

  As shown in FIG. 4, the insertion hole 47a1 (press-fit hole) of the first pinion shaft 47b provided in the first carrier base 47a is bottomed and is opposite to the open end 47b3 of the first pinion shaft 47b. , And a cover wall 47a2 covering the. As a result, the first pinion shaft 47b is prevented from facing the caliper 200 (see FIGS. 1 and 2) positioned below the first planetary gear mechanism 46B in FIG. According to such a configuration, it is possible to suppress the component of grease (lubricating oil) in the recess 47b1 (the housing portion) from reaching the caliper 200 through the infiltration path of the first pinion shaft 47b.

  As mentioned above, although the embodiment of the present invention was illustrated, the above-mentioned embodiment is an example and it is not intended to limit the range of the present invention. The above embodiment can be implemented in other various forms, and various omissions, replacements, combinations, and changes can be made without departing from the scope of the invention. In addition, the specifications (structure, type, direction, type, size, length, width, thickness, height, number, placement, position, material, etc.) of each configuration, shape, etc. are appropriately changed. Can be implemented.

  For example, the shape, size, length, number, and other specifications of the housing portion for housing the lubricating oil may be variously changed. When the housing portion is a recess, the open end of the recess may be covered or blocked by a member other than the first shaft fixed to the first shaft. In addition, the through hole (for example, the press-in hole) provided in the support member and into which the first shaft is inserted may be covered or blocked by a member other than the support member. Further, the lubricating oil is not limited to grease, and may be solid, liquid or the like.

  Further, in the case where the housing portion is a recess, the configuration in which the diameter of the recess decreases as approaching the root portion of the first shaft protruding from the support member does not have to be provided in the entire recess, and only the portion near the bottom of the recess May be provided.

  Further, the entire first shaft does not have to be a porous material, and at least a portion of the first shaft may be made of a porous material. The first shaft may include a porous material other than the sintered material. The infiltration path may be provided on only a portion of the first shaft. The first shaft may comprise a porous material and a non-porous material. In this case, the first shaft may have a configuration in which a divided body made of a porous material and a divided body made of a non-porous material are integrated. Also, the first shaft and the support member may be made of one porous material (sintered material) obtained by the same manufacturing process (for example, a sintering process) and not as separate members but as one member.

  20: Motor (drive source), 42: second planetary gear mechanism, 43: second sun gear, 44: second planetary carrier, 44b: second pinion shaft, 44c: second pinion gear, 44d: first sun gear, 45: Second ring gear, 46: first planetary gear mechanism, 47: first planetary carrier (gear mechanism), 47a: first carrier base (supporting member), 47b: first pinion shaft (first shaft), 47b1: recess (: Housing portion), 47b2: outer periphery, 47b3: opening end, 47c: first pinion gear (first gear), 48: first ring gear.

Claims (5)

A housing portion of lubricating oil is provided, and at least a portion is made of a porous metal material having an infiltration path through which at least a part of the component of the lubricating oil accommodated in the housing portion exudes to the outer periphery, With one shaft,
A first gear rotatably supported on the first shaft around the outer periphery;
Gear mechanism equipped with   The gear mechanism according to claim 1, further comprising a support member connected to the first shaft and made of a metal material having a density higher than that of the porous metal material.   A first sun gear, a first ring gear, a plurality of first pinion gears as the first gear meshed with the first sun gear and the first ring gear, and a first shaft supporting the plurality of first pinion gears The gear mechanism according to claim 1 or 2, further comprising: a first planetary gear mechanism having a first planetary carrier including a plurality of first pinion shafts.   A second planetary gear including a second sun gear, a second ring gear, a plurality of second pinion gears meshing with the second sun gear and the second ring gear, and a plurality of second pinion shafts supporting the plurality of second pinion gears. A carrier, and at least one of the second sun gear, the second ring gear, and the second planetary carrier is made of a synthetic resin material, and transmits rotation from a drive source to the first planetary gear mechanism A gear mechanism according to claim 3, comprising a two-planet gear mechanism. The first planetary gear mechanism and the second planetary gear mechanism overlap in the axial direction of the first pinion shaft;
The gear mechanism according to claim 4, wherein an open end of the accommodation portion facing the second planetary carrier is covered by the second planetary carrier.

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