JP2014001813A - Speed reduction mechanism and motor rotational force transmission device including the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a speed reduction mechanism capable of suppressing generation of inclination and wobble in a rotation axis, and to provide a motor rotational force transmission device including the same.SOLUTION: A reduction gear transmission mechanism 5 comprises a bearing mechanism A with a pair of ball bearings 35 and 38. In the bearing mechanism A, one ball bearing 35 and the other ball bearing 38 respectively support a flange 30c integrally provided in a differential case 30 and a flange 30f coupled to the flange 30c by a plurality of output members 53 so as to be rotatable to an outer peripheral surface of a motor shaft 42 on a radially inner side of each of the plurality of output members 53.

Description

  The present invention relates to a speed reduction mechanism suitable for use in, for example, an electric vehicle having an electric motor as a drive source, and a motor rotational force transmission device including the same.

  A conventional motor rotational force transmission device includes an electric motor that generates a motor rotational force, and a deceleration transmission mechanism that transmits a driving force based on the motor rotational force of the electric motor to a differential mechanism. (See, for example, Patent Document 1).

  The electric motor has a motor shaft that is rotated by the electric power of the in-vehicle battery, and is disposed on the axis of the deceleration transmission mechanism.

  The deceleration transmission mechanism has a shaft portion (rotating shaft with an eccentric portion) that is spline-fitted to the motor shaft of the electric motor, and a pair of deceleration transmission portions that are positioned around the rotating shaft with the eccentric portion. It is disposed between the moving mechanism (difference case) and connected to the motor shaft and the difference case. The deceleration transmission mechanism is accommodated in the housing together with the electric motor and the differential mechanism.

  With the above configuration, the motor shaft of the electric motor is rotated by the electric power of the in-vehicle battery, and accordingly, the motor rotational force is transmitted from the electric motor to the differential mechanism via the speed reduction transmission mechanism, and the left and right wheels are transmitted from this differential mechanism. To be distributed.

  By the way, the deceleration transmission part of this type of motor torque transmission device is a pair of disk-shaped revolving members that revolve by rotation of the motor shaft of the electric motor (rotation of the rotating shaft with an eccentric part). There are a plurality of outer pins for applying a rotation force, and a plurality of inner pins for outputting the rotation force of the revolution member as a rotational force to the differential mechanism inside the outer pins.

  The pair of revolving members have a center hole that opens in the direction of the center axis, and a plurality of pin insertion holes that are arranged at equal intervals around the center axis of the center hole, and are supported by the eccentric part of the rotary shaft with the eccentric part. It is rotatably supported via a (cam-side bearing).

  The plurality of outer pins are arranged at equal intervals around the axis of the motor shaft and are attached to the housing of the speed reduction transmission mechanism.

  The plurality of inner pins are inserted through a plurality of pin insertion holes in the revolving member, arranged at equal intervals around the axis of the motor shaft, and attached to the differential case. A bearing (pin side bearing) for reducing contact resistance between the inner peripheral surfaces of the plurality of pin insertion holes in the pair of revolution members is attached to the plurality of inner pins.

JP 2007-218407 A

  In the motor rotational force transmission device shown in Patent Document 1, it is not only necessary to prepare a plurality of outer pins, but the outer peripheral portion of the revolving member needs to have a complicated shape, which is uneconomical.

  Therefore, the revolution member is an external gear, and the rotation force imparting member for imparting a rotation force to the revolution member is an internal gear, and the number of teeth of the internal gear is larger than the number of teeth of the external gear. It is conceivable to eliminate the above-mentioned uneconomical as a number.

  However, when such a reduction gear composed of external gears and internal gears is used in a motor torque transmission device of an automobile, centrifugal force is applied from the external gears to the differential mechanism side end of the motor shaft (rotation shaft) during output. When the load due to was applied, the rotating shaft was tilted or swung. If the rotation shaft is tilted or shaken, the external gear may mesh with the internal gear in a tilted state, and smooth rotation of the differential case may be hindered.

  Accordingly, it is an object of the present invention to provide a speed reduction mechanism that can suppress the occurrence of tilt and vibration of a rotating shaft, and a motor torque transmission device including the speed reducing mechanism.

  In order to achieve the above object, the present invention provides a speed reduction mechanism (1) to (6) and a motor torque transmission device including the speed reduction mechanism.

(1) A rotating shaft having an eccentric portion, and an input member comprising an external gear having a plurality of through-holes that are rotatably arranged around the eccentric portion of the rotating shaft and are arranged at equal intervals around the axis. A rotation force imparting member that is meshed with the input member and includes an internal gear having a number of teeth larger than the number of teeth of the external gear, and a rotation force imparted to the input member by the rotation force imparting member. An output mechanism having a plurality of output members that are output as rotational forces to the output target and inserted through the plurality of through holes, respectively, and rolls that are arranged on the axis of the output mechanism and that face each other via the input member A bearing mechanism having a pair of inner bearings comprising a bearing, wherein the bearing mechanism includes a first flange integrally provided on the output target, wherein one inner bearing of the pair of inner bearings is also the First buttocks Of the pair of inner bearings, the other inner bearing supports the second flange connected by the plurality of output members rotatably on the outer peripheral surface of the rotary shaft on the radially inner side of the plurality of output members. Reduction mechanism.

(2) In the speed reduction mechanism described in (1) above, the bearing mechanism is configured such that the one inner bearing acts on an axial load acting on one side in the axial direction, and the other inner bearing acts on the other side in the axial direction. Axial loads are respectively received as preloads by connecting the first and second collars.

(3) In the reduction mechanism according to (2), the output mechanism includes a first fastening member for applying an axial load acting on one side in the axial direction to the one inner bearing, and the axial direction. The plurality of output members are formed by a screw member for screwing a second fastening member for applying an axial load acting on the other side to the other inner bearing.

(4) In the speed reduction mechanism according to (3), the output mechanism includes a first step surface that interposes the first flange portion with the first fastening member, and the second fastening. The plurality of output members have a second step surface in which the second flange portion is interposed between the plurality of output members.

(5) In the reduction mechanism according to any one of (1) to (4), the bearing mechanism includes a pair of outer bearings composed of rolling bearings facing each other via the input member, and the pair of pairs Of the outer bearings, one outer bearing serves as the first flange portion, and the other outer bearing serves as the second flange portion on the radially outer side of the plurality of output members. It is supported rotatably.

(6) In a motor rotational force transmission device comprising: an electric motor that generates a motor rotational force; and a reduction mechanism that decelerates the motor rotational force of the electric motor and outputs a driving force. A motor rotational force transmission device which is the speed reduction mechanism according to any one of 1) to (5).

  According to the present invention, it is possible to suppress the occurrence of tilt and shake of the rotating shaft.

The top view shown in order to demonstrate the outline of the vehicle carrying the motor rotational force transmission apparatus which concerns on the 1st Embodiment of this invention. Sectional drawing shown in order to demonstrate the whole motor rotational force transmission apparatus which concerns on the 1st Embodiment of this invention. FIG. 3 is a cross-sectional view schematically showing the deceleration transmission mechanism of the motor torque transmission device according to the first embodiment of the present invention. Sectional drawing which expands and shows the principal part (M part of FIG. 2) of the motor rotational force transmission apparatus which concerns on the 1st Embodiment of this invention. Sectional drawing shown in order to demonstrate the whole motor rotational force transmission apparatus which concerns on the 2nd Embodiment of this invention. Sectional drawing which expands and shows the principal part (N part of FIG. 5) of the motor rotational force transmission apparatus which concerns on the 2nd Embodiment of this invention.

[First embodiment]
Hereinafter, a speed reduction mechanism according to a first embodiment of the present invention and a motor torque transmission device including the speed reduction mechanism will be described in detail with reference to the drawings.

  FIG. 1 schematically shows a four-wheel drive vehicle. As shown in FIG. 1, a four-wheel drive vehicle 101 uses a front-wheel-side power system that uses a drive source as an engine, and a rear-wheel-side power system that uses a drive source as an electric motor. , An engine 102, a transaxle 103, a pair of front wheels 104, and a pair of rear wheels 105.

  The motor rotational force transmission device 1 is disposed in a power system on the rear wheel side of the four-wheel drive vehicle 101 and is supported by a vehicle body (not shown) of the four-wheel drive vehicle 101.

  The motor rotational force transmission device 1 transmits a driving force based on the motor rotational force of the electric motor 4 (described later) to the pair of rear wheels 105. As a result, the motor rotational force of the electric motor 4 is output to the rear axle shaft 106 (a pair of rear wheels 105) via the deceleration transmission mechanism 5 and the rear differential 3 (both described later), and the pair of rear wheels 105 are driven. Details of the motor rotational force transmission device 1 and the like will be described later.

  The engine 102 is disposed in the power system on the front wheel side of the four-wheel drive vehicle 101. As a result, the driving force of the engine 102 is output to the front axle shaft 107 (a pair of front wheels 104) via the transaxle 103, and the pair of front wheels 104 are driven.

(Whole structure of the motor torque transmission device 1)
FIG. 2 shows the entire motor torque transmission device. As shown in FIG. 2, the motor rotational force transmission device 1 includes a housing 2 having an axis O ₁ ( _first axis) as an axis of a rear axle shaft 106 (shown in FIG. 1), and a driving force based on the motor rotational force. The rear differential 3 distributed to the rear wheels 105 (shown in FIG. 1), the electric motor 4 that generates a motor rotational force for operating the rear differential 3, and the motor rotational force of the electric motor 4 is decelerated to reduce the driving force. It is mainly composed of a deceleration transmission mechanism 5 that transmits to the rear differential 3.

(Configuration of housing 2)
The housing 2 includes a rotation force applying member 52 to be described later, a first housing element 20 that houses the rear differential 3, a second housing element 21 that houses the electric motor 4, and a one-side opening of the second housing element 21. And a third housing element 22 that closes a portion (an opening on the side opposite to the opening on the first housing element 20 side).

The first housing element 20 is disposed on one side in the axial direction of the housing 2 (left side in FIG. 2), and is entirely formed by a stepped bottomed cylindrical member that opens to the second housing element 21 side. The bottom of the first housing element 20 is provided with a shaft insertion hole 20a through which the rear axle shaft 106 (shown in FIG. 1) is inserted, and an inner flange 20b protruding in the radial direction on the inner peripheral surface of the shaft insertion hole 20a. ing. The inner flange 20b is provided with an annular notch 20c that opens on the flange end surface on the second housing element 21 side of both flange end surfaces and the inner peripheral surface of the shaft insertion hole 20a. On the opening end surface of the first housing element 20, an annular convex portion 23 that protrudes toward the second housing element 21 is integrally provided. The outer peripheral surface of the convex portion 23 is formed by a circumferential surface having an outer diameter smaller than the maximum outer diameter of the first housing element 20 and having the axis O ₄ (fourth axis) as the central axis. The inner peripheral surface of the first housing element 20 is disposed between the outer peripheral surface of the rear axle shaft 106 and a seal member 24 that seals the shaft insertion hole 20a. In FIG. 2, the axis O ₄ is drawn to coincide with the axis O ₁ .

The second housing element 21 is disposed at an intermediate portion in the axial direction of the housing 2, and is entirely formed of a bottomless cylindrical member that opens in both directions of the axial line O ₄ . A stepped inner flange 21 a interposed between the electric motor 4 and the speed reduction transmission mechanism 5 is integrally provided at one side opening of the second housing element 21 (opening on the first housing element 20 side). ing. An annular member 25 for attaching a race is attached to the inner peripheral surface of the inner flange 21a. An annular convex portion 27 that protrudes toward the first housing element 20 is integrally provided on one side opening end surface of the second housing element 21 (opening end surface on the first housing element 20 side). The outer peripheral surface of the convex portion 27 is a circumferential surface having an outer diameter that is smaller than the maximum outer diameter of the second housing element 21 and substantially the same as the outer diameter of the convex portion 23 and that has the axis O ₄ as the central axis. Is formed.

  The third housing element 22 is disposed on the other side in the axial direction of the housing 2 (right side in FIG. 2), and is entirely formed of a stepped bottomed cylindrical member that opens to the second housing element 21 side. A shaft insertion hole 22 a through which the rear axle shaft 106 is inserted is provided at the bottom of the third housing element 22. A cylindrical portion 22b for attaching a stator that protrudes toward the electric motor 4 is integrally provided on the inner opening periphery of the shaft insertion hole 22a. The inner peripheral surface of the third housing element 22 is disposed between the outer peripheral surface of the rear axle shaft 106 and a seal member 28 that seals the shaft insertion hole 22a. The third housing element 22 is provided with an annular step surface 22 c that restricts the movement of the ball bearing 46 (outer ring 461) to the side opposite to the speed reduction transmission mechanism 5.

(Configuration of rear differential 3)
The rear differential 3 includes a bevel gear type differential mechanism having a differential case 30, a pinion gear shaft 31, a pair of pinion gears 32, and a pair of side gears 33, and is arranged on one side (left side in FIG. 2) of the motor torque transmission device 1. ing.

  As a result, the rotational force of the differential case 30 is distributed from the pinion gear shaft 31 to the side gear 33 via the pinion gear 32, and from the side gear 33 to the left and right rear wheels 105 (shown in FIG. 1) via the rear axle shaft 106 (shown in FIG. 1). ).

  On the other hand, when a driving resistance difference occurs between the left and right rear wheels 105, the rotational force of the differential case 30 is differentially distributed to the left and right rear wheels 105 by the rotation of the pinion gear 32.

The differential case 30 is disposed on the axis O ₅ (fifth axis), and rotates on the first housing element 20 via a ball bearing 34 and on the motor shaft 42 of the electric motor 4 via a ball bearing 35. Supported as possible. The differential case 30 receives the driving force based on the motor rotational force of the electric motor 4 from the deceleration transmission mechanism 5 and rotates around the axis O ₅ . In FIG. 2, the axis O ₅ is drawn to coincide with the axis O ₁ .

  The differential case 30 includes a housing space 30a that houses the differential mechanism (pinion gear shaft 31, pinion gear 32, and side gear 33), and a pair of shaft insertion holes 30b that communicate with the housing space 30a and connect the left and right rear axle shafts 106 respectively. Is provided.

  In addition, the differential case 30 is integrally provided with an annular flange 30 c as a first flange portion facing the speed reduction transmission mechanism 5. An annular step surface 30d that restricts the movement of the ball bearing 34 (inner ring 340) toward the motor shaft 42 is provided at one end in the axial direction of the differential case 30, and the speed reduction transmission mechanism 5 is provided at the other end in the axial direction. An annular concave hole 30e that opens to the side is provided. An annular step surface 300e that restricts the movement of the ball bearing 35 (outer ring 351) toward the differential case 30 is provided in the recessed hole 30e.

The flange 30c, the pin insertion hole 300c of a plurality (six in this embodiment) in parallel at equal intervals about the axis O ₁ is provided. On the side of the speed reduction transmission mechanism 5 of the flange 30c, a flange 30f is disposed as a second flange facing the flange end surface.

The flange 30f is connected to the flange 30c by a plurality of output members 53 on the axis of the motor shaft 42, and is rotatably supported on the outer peripheral surface of the motor shaft 42 via an annular spacer 37 and a ball bearing 38. Is formed by a stepped annular member. The flange 30f is provided with an accommodation hole 300f through which the motor shaft 42 is inserted and the spacer 37 and the ball bearing 38 are accommodated. Furthermore, the flange 30f movement of the pin insertion hole 301f of the plurality (six in this embodiment) in parallel at equal intervals about the axis O _1, and the electric motor 4 side of the ball bearing 38 (outer ring 381) An annular convex portion 302f that restricts the inside of the housing hole 300f is provided.

The pinion gear shaft 31 is disposed on the axis L perpendicular to the axis O ₁ in the accommodation space 30a of the differential case 30, and the rotation around the axis L and the movement in the axis L direction are restricted by pins (not shown).

  The pair of pinion gears 32 is rotatably supported by the pinion gear shaft 31 and is accommodated in the accommodating space 30 a of the differential case 30.

  The pair of side gears 33 are housed in the housing space 30a of the differential case 30 and are connected by spline fitting to a rear axle shaft 106 (shown in FIG. 1) that passes through the shaft insertion hole 30b. The pair of side gears 33 mesh with the pair of pinion gears 32 with their gear shafts orthogonal to the gear shafts of the pair of pinion gears 32.

(Configuration of electric motor 4)
The electric motor 4 includes a stator 40, a rotor 41, and a motor shaft 42 (a motor shaft with an eccentric portion), and is disposed on the other side (right side in FIG. 2) of the motor rotational force transmission device ₁ on the axis O1. The rear differential 3 is connected via a speed reduction transmission mechanism 5. The electric motor 4 has a stator 40 connected to an ECU (Electronic Control Unit: not shown). In the electric motor 4, the stator 40 receives a control signal from the ECU, generates a motor rotational force for operating the rear differential 3, and rotates the rotor 41 together with the motor shaft 42.

  The stator 40 is disposed on the outer peripheral side of the electric motor 4 and is attached to the inner flange 21 a of the second housing element 21 by mounting bolts 43.

  The rotor 41 is disposed on the inner peripheral side of the electric motor 4 and is attached to the outer peripheral surface of the motor shaft 42.

The motor shaft 42 has one end on the inner peripheral surface of the annular member 25 via a ball bearing 44 and a sleeve 45, and the other end on the inner peripheral surface of the third housing element 22. And are supported rotatably. The motor shaft 42 is disposed on the axis O _1, the whole is formed by a cylindrical shaft member for inserting the rear axle shaft 106 (shown in Figure 1).

An eccentric part 42a having a planar circular shape having an axis O ₂ (second axis) that is eccentric in parallel with the axis (axis O ₁ ) with an eccentric amount δ ₁ at one end in the axial direction of the motor shaft 42, and A planar circular eccentric portion 42b having an axis O ₂ ′ (second axis) eccentrically parallel to the axis O ₁ with an eccentric amount δ ₂ (δ ₁ = δ ₂ = δ) is integrally provided. In addition, an annular step surface 42 c that restricts the movement of the ball bearing 35 (inner ring 350) toward the speed reduction transmission mechanism 5 is provided at one end in the axial direction of the motor shaft 42. Then, the one of the eccentric portion 42a and the other of the eccentric portion 42b, is disposed in a position parallel with a regular intervals (180 °) about the axis O _1. That is, the one eccentric portion 42a and the other eccentric portion 42b have the same distance from the axis O ₂ to the axis O ₁ and the distance from the axis O ₂ ′ to the axis O ₁ , and the axis O ₂ and the axis O _2. It is arranged on the outer peripheral surface of the motor shaft 42 so that the distances around the axis O ₁ with the ′ are equal. Further, the eccentric portion 42a and the eccentric portion 42b is disposed in a position parallel along the direction of the axis O _1.

  The eccentric portion 42a is provided with a step surface 42e that restricts the movement of the inner ring 540 of the ball bearing 54 toward the electric motor 4 side.

  Similarly, the eccentric portion 42b is provided with a step surface 42g that restricts movement of the inner ring 560 of the ball bearing 56 toward the rear differential 3 side.

  A resolver 47 serving as a rotation angle detector interposed between the outer peripheral surface of the motor shaft 42 and the inner peripheral surface of the cylindrical portion 22b is disposed at the other end portion in the axial direction of the motor shaft 42. A sleeve 63 that restricts the movement of the inner ring 460 toward the speed reduction transmission mechanism 5 between the rotor 41 of the electric motor 4 and the ball bearing 46 (inner ring 460) is disposed at the other axial end of the motor shaft 42. It is arranged intervening. The resolver 47 has a stator 470 and a rotor 471 and is accommodated in the third housing element 22. The stator 470 is attached to the inner peripheral surface of the cylindrical portion 22b, and the rotor 471 is attached to the outer peripheral surface of the motor shaft 42.

(Configuration of deceleration transmission mechanism 5)
FIG. 3 shows the entire deceleration transmission mechanism. FIG. 4 shows a main part (bearing mechanism) of the motor torque transmission device. In the present embodiment, the deceleration transmission mechanism is an eccentric oscillating speed reducing mechanism, and is an involute speed reducing mechanism with a small number of teeth among the eccentric oscillating speed reducing mechanisms. A large reduction ratio can be obtained by using the eccentric oscillating speed reduction mechanism. As shown in FIGS. 2 to 4, the speed reduction transmission mechanism 5 includes a pair of input members 50 and 51, a rotation force applying member 52, an output mechanism 53 </ b> A (a plurality of output members 53), and a bearing mechanism A (ball bearings 35 and 38). ) And disposed between the rear differential 3 and the electric motor 4. As described above, the deceleration transmission mechanism 5 decelerates the motor rotational force of the electric motor 4 and transmits the driving force to the rear differential 3.

One input member 50 is an external gear having a center hole 50a with the axis O ₃ (third axis) as the center axis, is disposed on the rear differential 3 side of the other input member 51, and is center hole 50a. Between the inner peripheral surface and the eccentric portion 42a is rotatably supported via a ball bearing 54. Then, the one input member 50 receives a motor rotational force from the electric motor 4 and performs a circular motion (revolution motion around the axis O ₁ ) in the directions of arrows m ₁ and m ₂ having an eccentricity δ. 2 and 3, the axis O ₃ is drawn to coincide with the axis O ₂ .

One input member 50 is provided with a plurality (six in this embodiment) of pin insertion holes (through holes) 50b arranged in parallel at equal intervals around the axis O ₃ (axis O ₂ ). The hole diameter of the pin insertion hole 50 b is set to be larger than the dimension obtained by adding the outer diameter of the needle roller bearing 55 to the outer diameter of the output member 53.

  An annular inner flange 50d that protrudes from the inner peripheral surface of the center hole 50a and restricts the movement of the ball bearing 54 (outer ring 541) toward the rear differential 3 is provided at the end portion on the rear differential side of one input member 50. It has been.

The outer peripheral surface of one of the input member 50, the external teeth 50c is provided with an involute tooth profile of the pitch circle having a center axis corresponding to the axis O _3. Number of teeth _{Z 1} of the external teeth 50c is set to, for example, _Z 1 = 195.

The other input member 51 is formed of an external gear having a center hole 51a having the axis O ₃ ′ as a center axis, is disposed on the electric motor 4 side of the one input member 50, and has an inner peripheral surface of the center hole 51a. A ball bearing 56 is rotatably supported between the eccentric portion 42b. The other input member 51 receives a motor rotational force from the electric motor 4 and performs a circular motion (revolution motion around the axis O ₁ ) in the directions of arrows m ₁ and m ₂ having an eccentricity δ. 2 and 3, the axis O ₃ ′ is drawn to coincide with the axis O ₂ ′.

The other input member 51 is provided with a plurality (six in this embodiment) of pin insertion holes (through holes) 51b arranged in parallel at equal intervals around the axis O ₃ ′ (axis O ₂ ′). The hole diameter of the pin insertion hole 51 b is set to be larger than the dimension obtained by adding the outer diameter of the needle roller bearing 57 to the outer diameter of the output member 53.

  An annular inner flange 51 d that protrudes from the inner peripheral surface of the center hole 51 a and restricts the movement of the ball bearing 56 (outer ring 561) toward the electric motor 4 is provided at the motor side end of the other input member 51. ing.

On the outer peripheral surface of the other input member 51, external teeth 51c having a pitch circle involute tooth profile with the axis O ₃ ′ as the central axis are provided. Number of teeth _{Z 2} of the external teeth 51c is set to, for example, _Z 2 = 195.

The rotation force imparting member 52 is composed of a pair of internal gears whose central axis is the axis O ₄ (fourth axis), and is disposed between the first housing element 20 and the second housing element 21. The whole is formed by a bottomless cylindrical member that opens in both directions of the axis O ₄ and constitutes a part of the housing 2. The rotation force applying member 52 meshes with the pair of input members 50 and 51, and receives the rotation force in the directions of the arrows n ₁ and n _{2 on one} input member 50 that revolves by receiving the motor rotation force of the electric motor 4. Further, rotational forces in the directions of the arrows l ₁ and l ₂ are applied to the other input member 51, respectively. 2 and 3, the axis O ₄ is drawn to coincide with the axis O ₁ .

A rotation force applying member 52, the direction of the first fitting portion 52a, and the second fitting portion 52b is the axis O ₄ fitted to the outer peripheral surface of the projection 27 to be fitted to the outer peripheral surface of the convex portion 23 Are provided at predetermined intervals.

On the inner peripheral surface of the rotation force applying member 52, the pitch meshes with the external teeth 50 c of one input member 50 and the external teeth 51 c of the other input member 51, and the axis O ₄ (axis O ₁ ) is the central axis. Circular involute tooth-shaped inner teeth 52c are provided. Number of teeth _{Z 3} of the internal teeth 52c is set to, for example, _Z 3 = 208. Number of teeth _{Z 3} of the internal teeth 52c is set to, for example, _Z 3 = 208. The reduction ratio α of the deceleration transmission mechanism 5 is calculated from α = Z ₂ / (Z ₃ −Z ₂ ).

  The output mechanism 53A includes a plurality (six in this embodiment) of output members 53, is disposed between the rear differential 3 and the electric motor 4, and is accommodated in the housing 2.

The plurality of output members 53 are arranged at equal intervals around the axis O ₁ , and are inserted through the pin insertion hole 50 b of one input member 50 and the pin insertion hole 51 b of the other input member 51, and the flange 30 c of the differential case 30. It is attached to 30f. The plurality of output members 53 receive the rotation force applied by the rotation force applying member 52 from the pair of input members 50 and 51 and output the rotation force to the differential case 30 as the rotation force. The plurality of output members 53 include a screw portion 53a for screwing a nut 64 as a first fastening member, a screw portion 53b for screwing a nut 65 as a second fastening member, and both the screw portions 53a and 53b. A screw member comprising a stepped round shaft having adjacent shaft portions 53c and 53d, an intermediate portion 53e interposed between the shaft portions 53c and 53d, and a partition portion 53f that bisects the intermediate portion 53e in the axial direction. Used. Nut 64 is axially one side of the axial load P = P ₁ acting on the ball bearing 35 (the electric motor 4 side shown in FIG. 2), also nut 65 is axially other side (rear differential 3 side shown in FIG. 2) Axial load P = P ₂ (| P ₂ | = | P ₁ |) acting on the ball bearing 38 is applied to the ball bearing 38 as a preload. In FIG. 4, “P ₁ ” indicates the magnitude of the rightward load, and “P ₂ ” indicates the magnitude of the leftward load.

  The plurality of output members 53 include a step surface (first step surface) 53g interposed between the shaft portion 53c on one side (rear differential 3 side) and the intermediate portion 53e, and the other side (electric motor 4 side). A step surface (second step surface) 53h is provided between the shaft portion 53d and the intermediate portion 53e.

  The contact resistance with the inner peripheral surface of the pin insertion hole 50b in one input member 50 is formed on the outer peripheral surface of the intermediate portion 53e in the plurality of output members 53 and located on the rear differential 3 side of the partition portion 53f. Needle roller bearings 55 for reduction are attached. Further, the contact resistance of the other input member 51 with the pin insertion hole 51b is reduced on the outer peripheral surface of the intermediate portion 53e in the plurality of output members 53 and located on the electric motor 4 side of the partition portion 53f. Needle roller bearings 57 are attached.

The bearing mechanism A has a pair of ball bearings 35 and 38 as a pair of inner bearings that support the flanges 30 c and 30 f on the outer peripheral surface of the motor shaft 42 on the radially inner side of the plurality of output members 53. The differential case 30 is disposed at a position where it receives axial loads P = P ₁ and P ₂ acting in opposite directions as preloads by connecting the flanges 30 c and 30 f of the differential case 30.

The pair of ball bearings 35 and 38 are arranged to face each other on the axis O ₁ via one input member 50 and the other input member 51.

  One ball bearing 35 includes two inner and outer race rings 350 and 351 (inner ring 350 and outer ring 351) that are parallel to each other at the inner and outer peripheral portions thereof, and rolling elements 352 that roll between the inner ring 350 and the outer ring 351. The stepped surface 42c of the motor shaft 42 is disposed between the inner peripheral surface of the recessed hole 30e of the differential case 30 and the outer peripheral surface of one end in the axial direction of the motor shaft 42 on the rear differential 3 side.

  The inner ring 350 is attached to the outer peripheral surface of one end portion in the axial direction of the motor shaft 42 by an interference fit with the one end (electric motor 4 side) end surface 350a in contact with the eccentric portion 42a.

The outer ring 351 has one end (rear differential 3 side) end surface 351a in contact with the stepped surface 300e of the recessed hole 30e of the differential case 30, and is attached to the inner peripheral surface of the recessed hole 30e by clearance fitting. The outer ring 351 is recessed in the differential case 30 by screwing nuts 64 into the threaded portions 53a of the plurality of output members 53 inserted through the pin insertion holes 300c of the flange 30c and attaching (tightening) the flange 30c to the shaft portion 53c. An axial load P = P ₁ acting on one side (electric motor 4 side) in the axial direction from the step surface 300e of the hole 30e is applied as a preload.

  The rolling element 352 is disposed between the inner ring 350 and the outer ring 351, and is held by a cage 353 so as to be able to roll.

  Similarly, the other ball bearing 38 includes two inner and outer race rings 380 and 381 (inner ring 380 and outer ring 381) parallel to each other at the inner and outer peripheral portions thereof, and a rolling element 382 that rolls between the inner ring 380 and the outer ring 381. Between the inner peripheral surface of the housing hole 300f of the flange 30f and the outer peripheral surface of one end in the axial direction of the motor shaft 42 (spacer 37) on the electric motor 4 side of the eccentric portion 42b of the motor shaft 42. Are arranged.

  The inner ring 380 has an end surface 380a on one side (rear differential 3 side) brought into contact with the eccentric portion 42b (the flange portion 37a of the spacer 37), and becomes an outer peripheral surface of one end portion (spacer 37) in the axial direction of the motor shaft 42. Attached by fit.

The outer ring 381 is attached to the inner peripheral surface of the accommodation hole 300f by a clearance fit, with one end (electric motor 4 side) end surface 381a abutting against the convex portion 302f of the flange 30f. The outer ring 381 has a convex portion of the flange 30f by fitting (tightening) the flange 30f to the shaft portion 53d by screwing the nut 65 into the screw portions 53b of the plurality of output members 53 inserted through the pin insertion holes 301f of the flange 30f. An axial load P = P ₂ acting on the other side in the axial direction (rear differential 3 side) from the portion 302f is applied as a preload.

  The rolling element 382 is disposed between the inner ring 380 and the outer ring 381 and is held by a cage 383 so as to be able to roll.

In the bearing mechanism A of the motor torque transmission device 1 configured as described above, an axial load P = P ₁ is applied to one ball bearing 35 and an axial load P = P ₂ is applied to the other ball bearing 38 as a preload. Works.

  For example, the preload is applied to the ball bearings 35 and 38 as follows. Since the preload is applied to the ball bearings 35 and 38 in the present embodiment, the respective steps of “attaching the differential case side flange” and “attaching the electric motor side flange” are sequentially performed. To do. In the present embodiment, one input member 50 has a ball bearing 54 on the outer peripheral surface of the eccentric portion 42a, and the other input member 51 has a ball bearing 56 on the outer peripheral surface of the eccentric portion 42b. It is assumed that the flange 30c of the differential case 30 is previously supported on the outer peripheral surface of the motor shaft 42 via ball bearings 35, respectively.

“Attaching the differential case flange”
First, the plurality of output members 53 to which the needle roller bearings 55 and 57 are attached in advance are inserted into the pin insertion hole 50 b of one input member 50 and the pin insertion hole 51 b of the other input member 51. Next, the plurality of output members 53 are inserted into the pin insertion holes 300 c of the flange 30 c in the differential case 30. Thereafter, the nuts 64 are screwed into the insertion end portions (screw portions 53a) of the plurality of output members 53, and the flanges 30c are attached to the shaft portions 53c of the plurality of output members 53. At this time, the stepped surface 300e of the recessed hole 30e in the flange 30c presses the outer ring 351 of the ball bearing 35 against the electric motor 4 side as the nut 64 is screwed into the threaded portions 53a of the plurality of output members 53.

As a result, as shown in FIG. 4, the outer ring 351 of the ball bearing 35 receives the axial load P = P ₁ from the stepped surface 300e and moves to the electric motor 4 side, and the internal clearance in the axial direction of the ball bearing 35 disappears. Alternatively, the internal clearance in the axial direction of the ball bearing 35 is set as a negative clearance. In this case, the axial load P = P ₁ acts on the rolling element 352 on the rear differential 3 side from the center of the rolling element 352. In FIG. 4, the symbol a is the point of action of the axial load P = P _{1 on} the rolling element 352.

“Mounting the electric motor side flange”
First, the flange 30 f of the differential case 30 is supported on the outer peripheral surface of the motor shaft 42 via the spacer 37 and the ball bearing 38, and the plurality of output members 53 are inserted into the pin insertion holes 301 f of the flange 30 f in the differential case 30. Next, the nuts 65 are screwed into the insertion end portions (screw portions 53 b) of the plurality of output members 53, and the flanges 30 f are attached to the shaft portions 53 d of the plurality of output members 53. At this time, as the nut 65 is screwed into the threaded portions 53b of the plurality of output members 53, the convex portion 302f of the flange 30f presses the outer ring 381 of the ball bearing 38 against the rear differential 3 side.

Thus, as shown in FIG. 4, the outer ring 381 of the ball bearing 38 moves by receiving the protrusion 302f of the axial load P = P ₂ in the rear differential 3 side, there is no internal gap of the axial direction of the ball bearing 38, Alternatively, the internal clearance in the axial direction of the ball bearing 38 is set as a negative clearance. In this case, the axial load P = P ₂ acts on the rolling element 382 on the electric motor 4 side from the center of the rolling element 382. In FIG. 4, the symbol b is the point of action of the axial load P = P _{2 on} the rolling element 382.

(Operation of the motor rotational force transmission device 1)
Next, the operation of the motor torque transmission device shown in the present embodiment will be described with reference to FIGS.

  In FIG. 2, when electric power is supplied to the electric motor 4 of the motor rotational force transmission device 1 to drive the electric motor 4, the motor rotational force of the electric motor 4 is applied to the deceleration transmission mechanism 5 via the motor shaft 42. The deceleration transmission mechanism 5 operates.

Therefore, the speed reduction transmission mechanism 5 performs circular motion with a eccentricity δ is the input member 50, 51 in the arrow m ₁ direction shown in FIG. 3, for example.

Accordingly, the input member 50 is the axis _{O 2} while meshing with the internal teeth 52c of the outer teeth 50c rotation force applying member 52 counterclockwise (the arrow _{n 1} direction shown in FIG. 3), also the input member 51 outer teeth 51c respectively rotates to about a rotation force axis O ₂ while meshing with the internal teeth 52c of the applying member 52 _'(arrow l ₁ direction shown in FIG. 3). In this case, the rotation of the input members 50 and 51 causes the inner peripheral surface of the pin insertion hole 50b to be the race 550 of the needle roller bearing 55 and the inner peripheral surface of the pin insertion hole 51b to be the needle roller bearing as shown in FIG. 57 races 570 are in contact with each other.

  For this reason, the revolution movement of the input members 50 and 51 is not transmitted to the output member 53, but only the rotation movement of the input members 50 and 51 is transmitted, and the rotation force by this rotation movement is rotated from the output member 53 to the differential case 30. Output as power.

  As a result, the rear differential 3 is operated, and the driving force based on the motor rotational force of the electric motor 4 is distributed to the rear axle shaft 106 in FIG. 1 and transmitted to the left and right rear wheels 105.

In the above embodiment has described the case where the input member 50, 51 by circular motion of the arrow m ₁ direction to actuate the motor torque transmission device 1, the input member 50, 51 in the arrow m ₂ Direction Even if it makes a circular motion, the motor rotational force transmission device 1 can be operated in the same manner as in the above embodiment. In this case, the rotation of the input member 50 is performed in the direction of the arrow n ₂ , and the rotation of the input member 51 is performed in the direction of the arrow l ₂ .

[Effect of the first embodiment]
According to the first embodiment described above, the following effects can be obtained.

(1) Since the motor shaft 42 is supported by the differential case 30 by the ball bearings 35 and 38 that do not rattle in the radial direction, the motor shaft 42 is supported with respect to the differential case 30 (the axial center between the differential case 30 and the motor shaft 42). ) Is improved, and the occurrence of tilt and vibration during rotation of the motor shaft 42 can be suppressed.

(2) Since the rotation force imparting member 52 is formed by a cylindrical member that constitutes a part of the housing 2, the outer diameter of the rotation force imparting member 52 is larger than when the rotation force imparting member 52 is accommodated in the housing 2. Can be set to a large dimension, and the mechanical strength of the rotation force applying member 52 can be increased. In addition, the fact that the rotation force applying member 52 constitutes a part of the housing 2 can reduce the size in the radial direction of the entire apparatus and reduce the size.

(3) Centering is performed by fitting the first fitting portion 52a of the rotation force applying member 52 to the outer peripheral surface of the convex portion 23 and the second fitting portion 52b to the outer peripheral surface of the convex portion 27. Therefore, the manufacturing process of the rotation force applying member 52 can be easily performed.

[Second Embodiment]
Next, a motor torque transmission device according to a second embodiment of the present invention will be described with reference to FIGS. FIG. 5 shows the entire motor torque transmission device. FIG. 6 shows a main part of the motor torque transmission device. 5 and 6, members having the same or equivalent functions as those in FIGS. 2 and 4 are denoted by the same reference numerals, and detailed description thereof is omitted.

  As shown in FIGS. 5 and 6, the motor rotational force transmission device 100 according to the second embodiment of the present invention is characterized in that a bearing mechanism B is provided in addition to the bearing mechanism A as a bearing mechanism.

For this reason, the bearing mechanism B has ball bearings 66 and 67 as a pair of outer bearings that support the flanges 30c and 30f on the inner peripheral surface of the rotation force applying member 52 on the radially outer side of the plurality of output members 53. Axial loads P = P ₃ , P ₄ (| P ₃ | = | P ₄ |) acting in opposite directions due to the connection of the flanges 30c, 30f of the differential case 30 by a plurality of output members 53 are arranged at positions where they are received as preloads. Has been. In FIG. 6, “P ₃ ” indicates the magnitude of the rightward load, and “P ₄ ” indicates the magnitude of the leftward load.

  In the differential case 30, a convex portion 301c protruding on the rear differential 3 side is provided on the outer peripheral surface of the flange 30c, and a convex portion 303f protruding on the electric motor 4 side is provided on the outer peripheral surface of the flange 30f.

The pair of ball bearings 66 and 67 are arranged to face each other on the axis O ₁ via the one input member 50 and the other input member 51.

  One ball bearing 66 has two inner and outer race rings 660 and 661 (inner ring 660 and outer ring 661) parallel to each other at the inner and outer peripheral portions thereof, and rolling elements 662 that roll between the inner ring 660 and the outer ring 661. The internal force 52c of the rotating force applying member 52 is disposed on the rear differential 3 side between the inner peripheral surface of the rotating force applying member 52 and the outer peripheral surface of the flange 30c of the differential case 30.

The inner ring 660 is attached to the outer peripheral surface of the flange 30c by an interference fit such that one end (rear differential 3 side) end surface 660a abuts the convex portion 301c. The inner ring 660 is attached to (tightened) the nuts 64 by screwing the nuts 64 into the threaded portions 53a of the plurality of output members 53 inserted through the pin insertion holes 300c of the flange 30c, thereby attaching (tightening) the flange 30c to the shaft portion 53c. axial load P = P ₃ acting in the axial direction one side (the electric motor 4 side) is applied as a pre-load.

  The outer ring 661 is configured such that one end (rear differential 3 side) end surface 661a is in contact with the annular spacer 68 and the inner peripheral surface of the end portion on one side in the axial direction (rear differential 3 side) of the rotation force applying member 52 is provided. It is attached by The spacer 68 is disposed so as to be interposed between the outer ring 661 of the ball bearing 66 and the end surface on one side (rear differential 3 side) in the axial direction of the inner teeth 52 c of the rotation force applying member 52.

  The rolling element 662 is disposed between the inner ring 660 and the outer ring 661 and is held by a cage 663 so as to be able to roll.

  Similarly, the other ball bearing 67 includes two inner and outer race rings 670 and 671 (inner ring 670 and outer ring 671) parallel to each other at the inner and outer peripheral portions thereof, and a rolling element 672 that rolls between the inner ring 670 and the outer ring 671. The internal force 52c of the rotation force applying member 52 is disposed between the inner peripheral surface of the rotation force applying member 52 and the outer peripheral surface of the flange 30f of the differential case 30 on the electric motor 4 side.

The inner ring 670 is attached to the outer peripheral surface of the flange 30f by an interference fit with one end (electric motor 4 side) end surface 670a abutting against the convex portion 303f. By fitting (tightening) the flange 30f to the shaft portion 53d by screwing the nut 65 into the screw portions 53b of the plurality of output members 53 inserted through the pin insertion holes 301f of the flange 30f, the inner ring 670 can be removed from the convex portion 303f. axial load P = P ₄ acting to the other side in the axial direction (the rear differential 3 side) is given as preload.

  The outer ring 671 is configured such that one end (rear differential 3 side) end surface 671a is brought into contact with the annular spacer 69, and the outer ring 671 has a clearance on the inner peripheral surface of the end portion on the other axial direction side (electric motor 4 side) of the rotation force applying member 52. It is attached by The spacer 69 is disposed between the outer ring 671 of the ball bearing 67 and the end surface on the other side (the electric motor 4 side) in the axial direction of the inner teeth 52 c of the rotation force applying member 52.

  The rolling element 672 is disposed between the inner ring 660 and the outer ring 661 and is held by a cage 673 so as to be able to roll.

In the bearing mechanism A of the motor rotational force transmission apparatus 100 configured as described above, the axial load P = P ₁ is applied to one ball bearing 35 and the other ball bearing 38 is disposed radially inward of the plurality of output members 53. axial load P = _{P 2} acts as a preload, respectively. In the bearing mechanism B, and the radially outer side of the plurality of output members 53, the axial load P = P ₃ on one of the ball bearing 66, also axial load P = P ₄ acts as a preload each other ball bearing 67. In this case, the axial load P = P ₃ acts on the rolling element 662 on the rear differential 3 side from the center of the rolling element 662. In FIG. 6, the symbol c is an action point of the axial load P = P _{3 on} the rolling element 662. Further, the axial load P = P ₄ acts on the rolling element 672 on the electric motor 4 side from the center of the rolling element 672. In FIG. 6, the symbol d is an action point of the axial load P = P _{4 on} the rolling element 672.

  In order to apply the preload to the ball bearings 66 and 67, the steps of “attaching the differential case side flange” and “attaching the electric motor side flange” are sequentially performed as in the first embodiment. A preload is applied to the bearings 66 and 67. In the present embodiment, when the ball bearing 35 is interposed between the outer peripheral surface of the motor shaft 42 and the inner peripheral surface of the recessed hole 30e of the differential case 30, the inner peripheral surface of the rotation force applying member 52 and the flange 30c. A ball bearing 66 is interposed between the outer peripheral surface. Further, when the ball bearing 38 is interposed between the outer peripheral surface of the motor shaft 42 (the outer peripheral surface of the spacer 37) and the inner peripheral surface of the housing hole 300f of the flange 30f, the inner peripheral surface of the rotation force applying member 52 and the flange 30f A ball bearing 67 is interposed between the outer peripheral surface.

[Effect of the second embodiment]
According to the second embodiment described above, the same effects as the effects (1) to (3) shown in the first embodiment can be obtained. However, in the present embodiment, the flanges 30 c and 30 f of the differential case 30 are supported on the outer peripheral surface of the motor shaft 42 via the ball bearings 35 and 38 on the radially inner side of the plurality of output members 53, respectively. Since the flanges 30c and 30f are supported on the inner peripheral surface of the rotation force applying member 52 via the ball bearings 66 and 67 on the radially outer side of the plurality of output members 53, respectively, the differential case is compared with the first embodiment. The support state of the motor shaft 42 with respect to the motor 30 (the axial center between the differential case 30 and the motor shaft 42) is further improved, and the occurrence of tilt and vibration during rotation of the motor shaft 42 can be more effectively suppressed.

  As mentioned above, although the deceleration mechanism of this invention and the motor rotational force transmission apparatus provided with this were demonstrated based on said embodiment, this invention is not limited to said embodiment, It deviates from the summary. The present invention can be carried out in various modes as long as it is not, for example, the following modifications are possible.

(1) In the above embodiment, the distance and the axis _{O 2} from the axis _{O 2} to the axis _{O 1} 'equal to the distance from to the axis _{O 1,} and the axis _{O 2} and the axis _{O 2'} axis _{O 1} around the with one to equal the distance of the eccentric portion 42a and the other of the eccentric portion 42b is disposed on the outer periphery of the motor shaft 42, at a site away with a regular intervals (180 °) from each other in the axial line O ₁ around Although the case where the pair of input members 50 and 51 are disposed has been described, the present invention is not limited to this, and the number of input members can be changed as appropriate.

That is, when there are n (n ≧ 3) input members, in the virtual plane orthogonal to the axis of the electric motor (motor shaft), the axis of the first eccentric part, the axis of the second eccentric part,. Assuming that the axis of the nth eccentric part is sequentially arranged in one direction around the axis of the motor shaft, the distance from the axis of each eccentric part to the axis of the motor shaft is equal, and the first eccentric part, Each of the eccentric portions is formed so that the included angle formed by a line segment connecting the axes of the two eccentric portions adjacent to each other among the two eccentric portions,..., The n-th eccentric portion and the axis of the motor shaft is 360 ° / n. The n input members are disposed at the outer periphery of the motor shaft and at a part spaced about 360 ° / n around the axis O ₁ .

  For example, when there are three input members, the axis of the first eccentric part, the axis of the second eccentric part, and the axis of the third eccentric part are on the motor axis on a virtual plane orthogonal to the axis of the motor shaft. If it is sequentially arranged in one direction around the axis, the distance from the axis of each eccentric part to the axis of the motor shaft is equal, and the first eccentric part, the second eccentric part, and the third eccentric part Each eccentric part is arranged on the outer periphery of the motor shaft so that the included angle formed by the line connecting the axis line of two eccentric parts adjacent to each other and the axis line of the motor shaft is 120 °. Three input members are arranged at portions separated by an interval of 120 °.

(2) In the above embodiment, the case where the present invention is applied to the four-wheel drive vehicle 101 using both the engine 102 and the electric motor 4 as the drive source has been described. However, the present invention is not limited to this, and only the electric motor is used as the drive source. The present invention can also be applied to an electric vehicle that is a four-wheel drive vehicle or a two-wheel drive vehicle. The present invention can also be applied to a four-wheel drive vehicle having an engine, a first drive shaft by an electric motor, and a second drive shaft by an electric motor, as in the above embodiment.

(3) In the embodiment described above, the ball bearings 35 and 38, which are deep groove ball bearings, are used between the outer peripheral surface of the motor shaft 42 and the inner peripheral surfaces of the flanges 30c and 30f, respectively. Although the case where the ball bearings 66 and 67 which are deep groove ball bearings are respectively used for the surface and the outer peripheral surfaces of the flanges 30c and 30f has been described, the present invention is not limited to this, and balls other than the deep groove ball bearing are used instead of the deep groove ball bearing. A bearing or a roller bearing may be used. Examples of such ball bearings and roller bearings include angular contact ball bearings, needle roller bearings, rod roller bearings, cylindrical roller bearings, tapered roller bearings, and self-aligning roller bearings.

(4) In the above embodiment, the inner rings 350 and 380 of the ball bearings 35 and 38 are respectively attached to the outer peripheral surface of the motor shaft 42 with an interference fit, and the outer rings 351 and 381 of the ball bearings 35 and 38 are respectively connected to the flange 30c, Although the case where it was attached to the inner peripheral surface of 30f with a clearance fit has been described, the present invention is not limited to this, and even if any inner ring or outer ring is an interference fit with respect to the peripheral surface to which these are attached, It may be a clearance fit or an interference fit. Similarly, the inner and outer rings of the ball bearings 66 and 67 may be interference fit, clearance fit, or interference fit with respect to the peripheral surface to which they are attached.

DESCRIPTION OF SYMBOLS 1 ... Motor rotational force transmission apparatus, 2 ... Housing, 20 ... 1st housing element, 20a ... Shaft penetration hole, 20b ... Inner flange, 20c ... Notch, 21 ... 2nd housing element, 21a ... Inner flange, 22 3rd housing element, 22a ... Shaft insertion hole, 22b ... Cylindrical part, 22c ... Step surface, 23 ... Convex part, 24 ... Seal member, 25 ... Ring member, 27 ... Convex part, 28 ... Seal member, 3 ... rear differential, 30 ... differential case, 30a ... accommodation space, 30b ... shaft insertion hole, 30c ... flange, 300c ... pin insertion hole, 301c ... convex part, 30d ... step surface, 30e ... concave hole, 300e ... step surface, 30f ... Flange, 300f ... accommodating hole, 301f ... pin insertion hole, 302f, 303f ... convex part, 31 ... pinion gear shaft, 32 Pinion gear, 33 ... side gear, 34 ... ball bearing, 340 ... inner ring, 35 ... ball bearing, 350 ... inner ring, 350a ... one side end face, 351a ... one side end face, 351 ... outer ring, 352 ... rolling element, 353 ... cage, 37: spacer, 37a: collar, 38: ball bearing, 380 ... inner ring, 380a ... one end face, 381 ... outer ring, 381a ... one end face, 382 ... rolling element, 383 ... cage, 4 ... electric motor, 40 ... Stator, 41 ... Rotor, 42 ... Motor shaft, 42a, 42b ... Eccentric part, 42c ... Stepped surface, 42e ... Stepped surface, 42g ... Stepped surface, 43 ... Mounting bolt, 44 ... Ball bearing, 45 ... Sleeve, 46 ... Ball bearings, 460 ... inner ring, 461 ... outer ring, 47 ... resolver, 470 ... stator, 471 ... rotor, 5 ... deceleration transmission mechanism, 50, 51 ... input member, 50a, 51a ... center hole, 0b, 51b ... pin insertion hole, 50c, 51c ... external teeth, 50d, 51d ... inner flange, 52 ... autorotation force applying member, 52a ... first fitting portion, 52b ... second fitting portion, 53A ... output Mechanism, 53 ... Output member, 53a, 53b ... Screw part, 53c, 53d ... Shaft part, 53e ... Intermediate part, 53f ... Partition part, 53g, 53h ... Step surface, 54 ... Ball bearing, 540,541 ... Race ring ( Inner ring 540, outer ring 541), 55 ... needle roller bearing, 550 ... race, 56 ... ball bearing, 560, 561 ... race ring (inner ring 560, outer ring 561), 57 ... needle roller bearing, 570 race, 63 ... sleeve , 64, 65 ... nut, 66 ... ball bearing, 660 ... inner ring, 660a ... one end face, 661 ... outer ring, 661a ... one end face, 662 ... rolling elements, 663 ... cage, 67 ... ball bearing, 670 ... inner ring 670a ... one end face, 671 ... outer ring, 671a ... one end face, 672 ... rolling element, 673 ... retainer, 68, 69 ... spacer, 100 ... motor rotational force transmission device, 101 ... four-wheel drive vehicle, 102 ... engine, 103 ... transaxle, 104 ... front wheel, 105 ... rear wheel, 106 ... rear axle shaft, 107 ... front axle shafts, A, B ... bearing mechanism, a, b, c, d ... acting point, _L, O 1, _{O 2} , O ' ₂ , O ₃ , O ₄ ... axis, P ... axial load, δ, δ ₁ , δ ₂ ... eccentricity

Claims (6)

A rotating shaft having an eccentric portion;
An input member comprising an external gear having a plurality of through-holes arranged rotatably around the eccentric portion of the rotating shaft and arranged in parallel at equal intervals around the axis;
A rotation force applying member that is engaged with the input member and includes an internal gear having a number of teeth larger than the number of teeth of the external gear;
An output mechanism having a plurality of output members that receive the rotation force applied to the input member by the rotation force applying member and output the rotation force to an output target, and respectively insert the plurality of through holes,
A bearing mechanism having a pair of inner bearings that are arranged on the axis of the output mechanism and that are opposed to each other via the input member;
In the bearing mechanism, a first flange integrally provided on the output target is connected to one inner bearing of the pair of inner bearings, and the first flange is connected to the first flange by the plurality of output members. A speed reduction mechanism in which the other inner bearing of the pair of inner bearings rotatably supports the second flange portion on the outer peripheral surface of the rotating shaft on the radially inner side of the plurality of output members.   The bearing mechanism has an axial load acting on one side in the axial direction of the one inner bearing and an axial load acting on the other side in the axial direction of the other inner bearing as preloads, respectively. The speed reduction mechanism according to claim 1, wherein the speed reduction mechanism is received by connection with the second collar.   The output mechanism includes a first fastening member for applying an axial load acting on one side in the axial direction to the one inner bearing, and an axial load acting on the other side in the axial direction on the other inner bearing. The speed reduction mechanism according to claim 2, wherein the plurality of output members are formed by a screw member for screwing a second fastening member to be applied.   The output mechanism includes a first step surface that interposes the first flange portion with the first fastening member, and an intermediate portion of the second flange portion with the second fastening member. The speed reduction mechanism according to claim 3, wherein the plurality of output members have a second step surface.   The bearing mechanism has a pair of outer bearings composed of rolling bearings facing each other via the input member, and one outer bearing of the pair of outer bearings serves as the first flange portion and the other outer side. The speed reduction mechanism according to any one of claims 1 to 4, wherein the bearing rotatably supports the second flange portion on the inner peripheral surface of the rotation force applying member on the radially outer side of the plurality of output members. . An electric motor for generating motor rotational force;
A motor rotational force transmission device comprising a speed reduction mechanism that decelerates the motor rotational force of the electric motor and outputs a driving force;
The speed reduction mechanism is the speed reduction mechanism according to any one of claims 1 to 5. A motor rotational force transmission device.

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