JP2016003672A - Planetary gear train carrier - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a structure of a carrier of a planetary gear train capable of easily assembling a pinion gear.SOLUTION: A clearance (φA+B) formed between first wall surfaces 60 and rotatably accommodating therein a third planetary gear P3 is larger than a clearance (φA+C) between second wall surfaces 62 (φA+B>φA+C). This is because an eccentricity due to an oscillation that occurs when the third planetary gear P3 rotates is larger than a second clearance C necessary at a time of assembling the third planetary gear P3. A recess (60) is formed in each first wall surface 60 so as to secure a necessary dimension (=φA+B) when the third planetary gear P3 rotates, thereby making it possible to prevent the third planetary gear P3 from contacting a wall surface 56 during rotation and prevent wear due to the contact between the third planetary gear P3 and the wall surface 56.

Description

  The present invention relates to a carrier of a planetary gear device, and more particularly to a carrier structure in which a pinion gear can be easily assembled.

  A well-known planetary gear device is provided in a power transmission mechanism such as a stepped automatic transmission. Generally, a planetary gear device includes a sun gear, a pinion gear, a carrier that supports the pinion gear so as to rotate and revolve, and a ring gear that meshes with the sun gear via the pinion gear. Patent Document 1 discloses that a center plate having an insertion portion through which a pinion gear is inserted is provided in the vicinity of the center in the axial direction of the carrier, and the pinion gear is assembled to the center plate.

International Publication No. 2013/088880 JP 2013-170605 A JP 2009-281429 A JP 2012-177468 A

  By the way, in Patent Document 1, when the pinion gear is assembled to the carrier, the pinion gear is inserted at the position where the pinion shaft is inserted and then inserted through the pinion shaft. Here, when the pinion gear is arranged at the position where the pinion shaft is inserted, there is no mechanism for determining the position of the pinion gear, so the position of the pinion gear is not determined, and there is a possibility that it takes time to assemble.

  The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a carrier structure in which a pinion gear can be easily assembled in a carrier of a planetary gear device.

  To achieve the above object, the gist of the first invention is that: (a) a carrier having a pair of guide members for rotatably holding a pinion gear of a planetary gear device provided in a vehicle and guiding the pinion gear; In (b) the pair of guide members, the pinion gear is interposed between the pair of guide members, and the pinion gear is guided to be disposed at a pinion gear assembly position. (C) The pinion gear assembly position is A position where the pinion shaft is inserted into the pinion gear; (d) the pair of guide members have different clearance portions between the pair of guide members; and (e) the clearance portion is formed by the pinion gear. A first clearance having a dimension such that the pinion gear and the guide member do not come into contact with each other when rotated, and smaller than the first clearance. A second clearance having a larger dimension than an outer diameter of the pinion gear; and (f) the first clearance is a portion of the pair of guide members where the assembly position of the pinion gear is interposed between the pair of guide members. (G) The second clearance is provided in a portion of the pair of guide members that guides the pinion gear to the pinion gear assembly position.

  As described above, the first clearance and the second clearance smaller than the first clearance and larger than the outer diameter of the pinion gear are formed between the pair of guide members, and the first clearance is between the pair of guide members. And the second clearance is provided at a portion for guiding the pinion gear to the pinion gear assembly position. Thus, when the pinion gear is assembled, the pinion gear can be guided from between the pair of guide members formed with the second clearance to the pinion gear assembly position. Thus, the pinion gear can be assembled by moving the pinion gear easily to the pinion gear assembly position.

1 is a skeleton diagram of a vehicle power transmission device provided in a vehicle to which the present invention is applied. It is sectional drawing of the carrier of FIG. It is AA sectional drawing of the carrier of FIG. It is sectional drawing of the carrier which is another Example of this invention. It is sectional drawing of the carrier which is another Example of this invention.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. In the following embodiments, the drawings are appropriately simplified or modified, and the dimensional ratios, shapes, and the like of the respective parts are not necessarily drawn accurately.

  FIG. 1 shows a part of a vehicle drive device 10 provided in a vehicle 6 to which the present invention is applied. The torque converter 12 and the vehicle are inserted on a power transmission path between an engine 8 and drive wheels. 1 is a skeleton diagram of an automatic transmission 14 (hereinafter, automatic transmission 14).

  The torque converter 12 is interposed between the engine 8 and the automatic transmission 14. The torque converter 12 is connected to a case 18 that is a non-rotating member via a pump impeller 12p connected to the engine 8, a turbine impeller 12t connected to the turbine shaft 16 of the automatic transmission 14, and a one-way clutch OWC. This is a well-known fluid transmission device including a stator impeller 12s. Further, a lockup clutch 20 that selectively connects and disconnects between the pump impeller 12p and the turbine impeller 12t is provided.

  The automatic transmission 14 includes, in a case 18, a first transmission unit 24 mainly composed of a single pinion type first planetary gear unit 22, a first brake B1, and a third brake B3, and a double pinion type first planetary gear unit. The second planetary gear unit 26, the single pinion type third planetary gear unit 28, the first clutch C1, the second clutch C2, and the second transmission unit 30 mainly composed of the second brake B2 are connected to a common shaft. It is configured to be provided on the heart C.

  The first planetary gear unit 22 includes a first sun gear S1, a first planetary gear P1, a first carrier CA1 that supports the first planetary gear P1 so as to rotate and revolve, and a first planetary gear P1 through the first planetary gear P1. A first ring gear R1 meshing with one sun gear S1 is included. Each of these gears (gears) is composed of inclined teeth.

  The second planetary gear unit 26 includes a second sun gear S2, a second planetary gear P2 (short pinion gear), a third planetary gear P3 (long pinion gear) described later, and the second planetary gear P2 and the third planetary gear P3. It includes a second carrier CA2 that is supported so as to be able to rotate and revolve, and a second ring gear R2 that meshes with the second sun gear S2 via the second planetary gear P2. Each of these gears (gears) is composed of inclined teeth.

  The third planetary gear device 28 (the planetary gear device of the present invention) includes a third sun gear S3, a third planetary gear P3 (long pinion gear), and a third carrier CA3 that supports the third gear P3 so as to be capable of rotating and revolving. And a third ring gear R3 that meshes with the third sun gear S3 via the third planetary gear P3. Each of these gears (gears) is composed of inclined teeth. The third planetary gear P3 corresponds to the pinion gear of the present invention.

  In the second transmission unit 30, the second planetary gear P2 (short pinion gear) and the third planetary gear P3 (long pinion gear) mesh with each other, so that a gear pair of the double pinion type second planetary gear device 26 is configured. The second carrier CA2 and the third carrier CA3 are connected to each other and integrated, and the second ring gear R2 and the third ring gear R3 are connected to each other to become a so-called Ravigneaux type planetary gear device. Yes. Thus, since the 2nd transmission part 30 is comprised with a Ravigneaux type planetary gear apparatus, the 2nd transmission part 30 becomes compact.

  The first sun gear S <b> 1 of the first planetary gear device 22 is connected to the turbine shaft 16. The first carrier CA1 is coupled to the second sun gear S2 of the second planetary gear device 26, and is configured to be selectively connectable to the case 18 that is a non-rotating member via the first brake B1. The first ring gear R1 of the first planetary gear device 22 is configured to be selectively connectable to the case 18 via the third brake B3. The second carrier CA2 of the second planetary gear device 26 and the third carrier CA3 of the third planetary gear device 28 are coupled to each other and connected to the output rotating member 32. The second planetary gear device 26 and the third planetary gear device 28 use a second ring gear R2 that is a common member, and are configured to be selectively connectable to the case 18 via the second brake B2. The turbine shaft 16 can be selectively connected via the second clutch C2. Further, the second ring gear R2 and the third ring gear R3 are connected to the case 18 via a one-way clutch OWC provided in parallel with the second brake B2. The third sun gear S3 of the third planetary gear device 28 is configured to be selectively connectable to the turbine shaft 16 via the first clutch C1.

  The automatic transmission 14 includes the two clutches C1 and C2 and the three brakes B1 to B3 (hereinafter, simply referred to as the clutch C and the brake B unless otherwise distinguished). By being engaged and released respectively, the connection state of the rotating elements (sun gears S1 to S3, carriers CA1 to CA3, ring gears R1 to R3) of the first transmission unit 24 and the second transmission unit 30 is changed. Six forward shift stages from the first shift stage “1st” to the sixth shift stage “6th” are established, and the reverse shift stage “Rev” is established. The clutch C and the brake B are hydraulic friction engagement devices that are controlled by a hydraulic actuator such as a multi-plate clutch or brake. Etc. are controlled.

  The second carrier CA2 of the second planetary gear device 26 and the third carrier CA3 of the third planetary gear device 28 described above are connected and integrated to form one structure (hereinafter referred to as carrier CA-a). Has been. Hereinafter, the structure of the carrier CA-a will be described.

  FIG. 2 is a cross-sectional view of the carrier CA-a (corresponding to the carrier of the present invention). The carrier CA-a includes a first carrier member 40, a second carrier member 42 that is connected to the first carrier member 40 in the axial direction, and a third carrier member 46 that is disposed on the outer peripheral side of the second carrier member 42. And these members are connected together to form a single unit.

  The first carrier member 40 includes a shaft insertion portion 40a through which the pinion shaft is inserted, and four connection portions 40b extending in the axial direction from the outer peripheral portion of the shaft insertion portion 40a. The first carrier member 40 is formed by, for example, sintering.

  The shaft insertion portion 40a includes four first shaft holes 48 through which a pinion shaft for rotatably supporting the second planetary gear P2 (short pinion gear) and a third planetary gear P3 (long pinion gear). Four second shaft holes 50 through which pinion shafts for rotatably supporting are inserted are formed. The first shaft holes 48 and the second shaft holes 50 are alternately arranged in the circumferential direction.

  The connecting portion 40b has a fan-like cross section when viewed from the axial direction, and is arranged at equiangular intervals in the circumferential direction. Further, the end of the connecting portion 40 b opposite to the shaft insertion portion 40 a in the axial direction is connected to the second carrier member 42 and the third carrier member 46.

  The second carrier member 42 is disposed on the opposite side of the carrier in the axial direction of the first carrier member 40, and includes a shaft insertion portion 42a through which the pinion shaft is inserted, and four connecting portions extending in the axial direction from the shaft insertion portion 42a. 42b. The second carrier member 42 is formed by sintering, for example. A pair of guide members for guiding the pinion gear of the present invention is configured by the connecting portions 42b adjacent in the circumferential direction.

  The shaft insertion portion 42a is formed with four fourth shaft holes 54 through which a pinion shaft for rotatably supporting the third planetary gear P3 (long pinion gear) is formed in the circumferential direction. Four third shaft holes 52 through which a pinion shaft for rotatably supporting the second planetary gear P2 (short pinion gear) is inserted are formed in the circumferential direction. The third shaft holes 52 and the fourth shaft holes 54 are alternately arranged in the circumferential direction. The first shaft hole 48 and the third shaft hole 52 are formed at the same rotational position (rotational phase), and the second shaft hole 50 and the fourth shaft hole 54 are disposed at the same rotational position (rotational phase). Is done. Therefore, both ends of the pinion shaft that rotatably supports the second planetary gear P2 are held by the first shaft hole 48 and the third shaft hole 52, and both ends of the pinion shaft that rotatably supports the third planetary gear P3. The second shaft hole 50 and the fourth shaft hole 54 are held.

  As will be described later, the connecting portion 42b of the second carrier member 42 has a fan-shaped cross section when viewed from the axial direction, and is formed at four equiangular intervals in the circumferential direction. Moreover, the connection part 42b is arrange | positioned in the position used as the same phase in the circumferential direction as the connection part 40b of the 1st carrier member 40, the axial end surface (mating surface) of the connection part 40b, and the axis | shaft of the connection part 42b The direction end face (mating face) is connected.

  The third carrier member 46 includes a disc portion 46a formed in an annular plate shape and a cylindrical tube portion 46b extending in the axial direction from the outer peripheral end portion of the disc portion 46a. The third carrier member 46 is formed by sintering, for example.

  In the axial direction of the disk portion 46 a of the third carrier member 46, the end portion on the pinion gear side is in contact with the end surface (matching surface) of the connecting portion 40 b of the first carrier member 40. Further, the inner peripheral end surface of the disc portion 46 a is brought into contact with the connecting portion 42 b of the second carrier member 42. In this state, the connecting portion 40b of the first carrier member 40, the connecting portion 42b of the second carrier member 42, and the disc portion 46a of the third carrier member 46 are connected to each other, for example, by brazing.

  FIG. 3 is a cross-sectional view of the carrier CA-a in FIG. As shown in FIG. 3, four connecting portions 42b having a fan-like cross section when viewed from the axial direction are formed at equal angular intervals in the circumferential direction, and third shaft holes 52 are formed in the respective connecting portions 42b. Has been. Moreover, the wall surface 56 is formed in the both sides of the circumferential direction of each connection part 42b. In addition, the cross-section when the connecting portion 42b is viewed from the axial direction is not strictly symmetrical with respect to the fan-shaped square bisector, and the portion where strength is required is appropriately thickened. Designed to be thick.

  Of the four connecting portions 42b, a pair of wall surfaces 56 (opposing surfaces) facing each other between a pair of adjacent connecting portions 42b are formed in parallel to each other and guide the third planetary gear P3 to the assembly position. Functions as a guide surface. That is, a pair of guide members for guiding the third planetary gear P3 is constituted by a pair of adjacent connecting portions 42b. Between the connecting portions 42b (wall surface 56) facing each other, clearance portions having different dimensions are formed by forming the first wall surface 60 and the second wall surface 62. Specifically, the first clearance having a dimension that does not allow the third planetary gear P3 and the connecting portion 42b to come into contact with each other between the pair of connecting portions 42b (wall surface 56) facing each other when the third planetary gear P3 rotates after assembly. A second clearance X2 that is smaller than the first clearance X1 and larger than the outer diameter φA of the third planetary gear P3 is formed. The first clearance X1 is provided in a portion (first wall surface 60) where the assembly position of the third planetary gear P3 is interposed between the wall surfaces 56 of the pair of connecting portions 42b facing each other. On the other hand, the 2nd clearance X2 is provided in the site | part (2nd wall surface 62) guided to the assembly position of the 3rd planetary gear P3 among the wall surfaces 56 of a pair of connection part which mutually faces.

  A circle indicated by a broken line in FIG. 3 indicates the third planetary gear P3 after assembly. That is, it corresponds to the assembly position of the third planetary gear P3. When the third planetary gear P3 is assembled, the third planetary gear P3 is disposed in a space that rotatably accommodates the third planetary gear P3 formed by the first wall surface 60 indicated by a broken line. The first wall surface 60 is formed with an arcuate recess (60) for securing a dimension necessary for rotatably accommodating the third planetary gear P3. When the outer diameter of the third planetary gear P3 is φA, the distance between the first wall surfaces 60 facing each other (centering around the rotational axis X of the third planetary gear P3) corresponds to the first clearance X1. The dimension of the first clearance X1 is experimentally set in advance so that when the third planetary gear P3 rotates, the third planetary gear P3 and the connecting portion 42b do not come into contact with the outer diameter φA of the third planetary gear P3. Is set to a value (φA + B) obtained by adding the predetermined dimension B obtained. The predetermined dimension B is set to a minimum value or a value in the vicinity thereof in a range where the third planetary gear P3 and the first wall surface 60 do not come into contact with each other when the third planetary gear P3 is rotated in the assembled state. Yes. Specifically, the predetermined dimension B takes into consideration the whirling during rotation of the third planetary gear P3, the dimensional tolerance of the third planetary gear P3, and the like, and the third planetary gear P3 whirls, and the third planetary gear P3. Even if the outer diameter of P3 is an allowable maximum value, it is set to a value at which the first wall surface 60 and the third planetary gear P3 do not contact each other.

  The second wall surface 62 is formed adjacent to both sides (the inner peripheral side and the outer peripheral side) of the first wall surface 60, and the second wall surfaces 62 facing each other are formed in parallel. Further, a gap formed between the second wall surfaces 62 facing each other corresponds to the second clearance X2, and the dimension thereof is the same as the outer diameter dimension φA of the third planetary gear P3, and the third planetary gear P3 is connected. It is set to a dimension (φA + C) that is smaller than a dimension necessary for rotating without contacting the portion 42b, that is, a predetermined dimension C that is smaller than the predetermined dimension B. This predetermined dimension C is experimentally obtained in advance, and considering the dimensional tolerance of the third planetary gear P3, even if the outer diameter of the third planetary gear P3 is the maximum allowable value, The distance is set to a value that can guide the third planetary gear P3 (a value that can be assembled). As a result, when the third planetary gear P3 is assembled, the third planetary gear P3 can be moved along the second wall surface 62. Accordingly, when the third planetary gear P3 is assembled to the carrier CA-a, the third planetary gear P3 is moved along the second wall surface 62 toward the assembly position between the second clearances X2. It is possible to easily guide the third planetary gear P3 to the assembly position, that is, the position accommodated in the space having the first clearance X1 formed by the first wall surface 60.

  As described above, the first clearance X1 (φA + B) formed between the first wall surfaces 60 that rotatably accommodate the third planetary gear P3 is the second clearance X2 (φA + C) formed between the second wall surfaces 62. (ΦA + B> φA + C). This is because the amount of eccentricity caused by the run-out generated when the third planetary gear P3 rotates is larger than the predetermined dimension C required when the third planetary gear P3 is assembled. Then, a recess (60) is formed on the first wall surface 60 so as to ensure the first clearance X1 (= φA + B) required when the third planetary gear P3 rotates, so that the third planetary gear is formed. P3 is prevented from contacting the wall surface 56 during rotation, and wear due to contact between the third planetary gear P3 and the wall surface 56 is prevented. Further, since the second clearance X2 (φA + C) formed between the second wall surfaces 62 facing each other is smaller than the dimension (φA + B) required for the rotation of the third planetary gear P3, the third planetary gear P3 is moved. Since the interval (φA + C) is reduced within a possible range, the cross-sectional area of the connecting portion 42b can be increased accordingly. Therefore, the rigidity of the carrier CA-a can be ensured.

  Next, assembly of the third planetary gear P3 to the carrier CA-a will be described. In the carrier CA-a of the present embodiment, since the cylindrical portion 46b is formed on the outer peripheral side of the carrier CA-a, the third planetary gear P3 cannot be assembled from the outer peripheral side. Accordingly, the third planetary gear P3 is moved from the inner peripheral side of the carrier CA-a along the second wall surface 62 toward the outer peripheral side. As described above, the third planetary gear P3 is moved along the second wall surface 62. At this time, the predetermined dimension C between the adjacent second wall surface 62 and the third planetary gear P3 is also small. Positioning of P3 becomes easy. Then, when the third planetary gear P3 moves to the position where it is accommodated in the first wall surface 60 (that is, the assembly position), the pinion shaft is inserted through the second shaft hole 50, the fourth shaft hole 54, and the third planetary gear P3. Thus, the third planetary gear P3 is assembled to the carrier CA-a.

  As described above, according to the present embodiment, the first clearance X1 between the pair of connecting portions 42b and the first clearance X1 smaller than the first clearance X1 and larger than the outer diameter φA of the third planetary gear P3. 2 clearance X2 is formed, and the first clearance X1 is provided at a position where the assembly position of the third planetary gear P3 is interposed between the pair of connecting portions 42b, and the second clearance X2 connects the third planetary gear P3 to the pinion gear. It is provided at the site that guides to the assembly position. Thus, when the third planetary gear P3 is assembled, the third planetary gear P3 can be guided from between the pair of connecting portions 42b in which the second clearance X2 is formed to the pinion gear assembly position. Thus, the third planetary gear P3 can be assembled by easily moving the third planetary gear P3 to the pinion gear assembly position.

  Next, another embodiment of the present invention will be described. In the following description, parts common to those in the above-described embodiment are denoted by the same reference numerals and description thereof is omitted.

  FIG. 4 is a cross-sectional view of a carrier CA-b (corresponding to the carrier of the present invention) which is another embodiment of the present invention, and corresponds to FIG. 2 of the above-described embodiment. When the carrier CA-b of the present embodiment is compared with the carrier CA-a of the above-described embodiment, the structure of the second carrier member 70 (the second carrier member 42 in the above-described embodiment) is different.

  The second carrier member 70 includes a shaft insertion portion 70a through which the pinion shaft is inserted, and four connection portions 70b extending in the axial direction from the shaft insertion portion 70a. The second carrier member 70 is also formed by sintering. The connecting portion 70b corresponds to the guide member.

  A conical taper 72 is formed on the outer peripheral side of the connecting portion 70b. The carrier CA-b is reduced in weight by the amount that the taper 72 is formed. Moreover, although the intensity | strength of the vicinity falls by the part which taper 72 is formed, since the site | part in which the 3rd shaft hole 52 is formed has sufficient dimension in an axial direction, intensity | strength is ensured. That is, since the strength is required in the vicinity of the third shaft hole 52 that supports the pinion shaft, the strength is secured by securing the axial thickness of the portion. Thus, the connection part 70b does not necessarily need to have the same dimension in an axial direction, and may change in an axial direction. Since other configurations are basically the same as the carrier CA-a described above, the description thereof is omitted.

  As described above, even with the carrier CA-b of this embodiment, the same effect as that of the above-described embodiment can be obtained. Furthermore, by forming the taper 72, the carrier CA-b is reduced in weight.

  FIG. 5 is a cross-sectional view of a carrier CA-c (corresponding to the carrier of the present invention) which is still another embodiment of the present invention, and corresponds to FIG. 3 of the above-described embodiment. When the carrier CA-c of this embodiment is compared with the carrier CA-a of the above-described embodiment, the structure of the second carrier member 80 (the second carrier member 42 in the above-described embodiment) is different. In the second carrier member 80 of this embodiment, a notch 82 is formed on the outer peripheral portion thereof. Accordingly, the cross-sectional area of the connecting portion 80b of the second carrier member 80 is a shape in which a part of the outer periphery is cut out from the fan shape. The connecting portion 80b corresponds to the guide member of the present invention.

  Here, the portion where the third shaft hole 52 is formed and the vicinity of the wall surface 56 require strength, but in the connecting portion 80b, the rigidity is ensured by forming these portions thick. ing. As described above, the portion requiring strength is formed thick, and the portion where strength is relatively not required is formed with the notch 82, so that the cross-sectional shape of the connecting portion 80b is suitably changed according to the required strength. Has been.

  In the carrier CA-c described above, the same effect as in the above-described embodiment can be obtained. Moreover, the rigidity of the carrier CA-c is suitably ensured by securing the thickness of the portion requiring rigidity.

  As mentioned above, although the Example of this invention was described in detail based on drawing, this invention is applied also in another aspect.

  For example, in the above-described embodiments, the embodiments can be appropriately combined. For example, the structure in which the connecting portion 70b of the carrier CA-b of the above-described embodiment is changed in the axial direction may be combined with the structure in which the cross section of the connecting portion 80b of the carrier CA-c is changed according to the strength. it can.

  In the above-described embodiments, the carriers CA-a, CA-b, and CA-c are used in Ravigneaux type planetary gear devices, but are not necessarily limited to Ravigneaux type planetary gear devices. The invention can be applied even to a planetary gear device of a single pinion type or a double pinion type.

  Further, for example, the cross-sectional shape of the connecting portion 42b in the above-described embodiment is formed in a fan shape, but the cross-section when the connecting portion 42b is viewed from the axial direction is not limited to this, for example, a trapezoid or The shape is changed as appropriate within a range in which the opposing wall surfaces 56, such as a quadrangle, are formed, that is, the second guide surface 62 that guides the third planetary gear P3 and the first guide surface 62 that forms a space for housing the third planetary gear P3. It doesn't matter.

  In the above-described embodiment, the first carrier member 40 to the third carrier member 46 constituting the carriers CA-a, CA-b, and CA-c are formed by sintering. For example, the third carrier member 46 can be appropriately changed, for example, formed by pressing. The carriers CA-a, CA-b, and CA-c are configured as one member by connecting the three members of the first carrier member 40 to the third carrier member 46 to each other. The number of members to be configured is not particularly limited, for example, the second carrier member 42b and the third carrier member 46b are integrally formed by sintering.

  Further, in the above-described embodiment, the cross-sectional shape of the connecting portion 42b is formed asymmetrical, but the present invention is not necessarily limited to the asymmetrical shape and may be configured symmetrically.

  In the above-described embodiment, four connecting portions 42b are formed at equiangular intervals in the circumferential direction. However, the number of connecting portions 42b is not necessarily limited to four, and three or five or more connecting portions 42b are formed. It doesn't matter. Specifically, it is appropriately changed according to the number of planetary gears.

  Moreover, in the above-mentioned Example, although the hollow (60) is formed in circular arc shape, the shape of a hollow is not necessarily limited to circular arc shape.

  In the above-described embodiment, the first planetary gear device 22, the second planetary gear device 26, and the third planetary gear device 28 are all configured with bevel teeth, but are not necessarily limited to bevel teeth. For example, it may be constituted by other types of gears such as spur gears.

  The above description is only an embodiment, and the present invention can be implemented in variously modified and improved forms based on the knowledge of those skilled in the art.

6: Vehicle 28: Third planetary gear device (planetary gear device)
42b, 70b, 80b: connecting portion (guide member)
P3: Third planetary gear (pinion gear)
CA-a, CA-b, CA-c: Carrier X1: First clearance X2: Second clearance

Claims (1)

A carrier comprising a pair of guide members for rotatably holding a pinion gear of a planetary gear device provided in a vehicle and guiding the pinion gear,
The pair of guide members interpose the pinion gear between the pair of guide members, and guide the pinion gear to be disposed at a pinion gear assembly position;
The pinion gear assembly position is a position where a pinion shaft is inserted into the pinion gear;
The pair of guide members have different clearance portions between the pair of guide members,
The clearance portion has a first clearance dimension that prevents the pinion gear from contacting the guide member when the pinion gear rotates, and a second clearance dimension that is smaller than the first clearance and larger than the outer diameter of the pinion gear. Have
The first clearance is provided in a portion of the pair of guide members that interposes the assembly position of the pinion gear between the pair of guide members,
The second clearance is provided in a portion of the pair of guide members that guides the pinion gear to the pinion gear assembly position.

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