JP2013117284A - Speed reduction mechanism, and motor torque transmission device including the same - Google Patents

Speed reduction mechanism, and motor torque transmission device including the same Download PDF

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Publication number
JP2013117284A
JP2013117284A JP2011265591A JP2011265591A JP2013117284A JP 2013117284 A JP2013117284 A JP 2013117284A JP 2011265591 A JP2011265591 A JP 2011265591A JP 2011265591 A JP2011265591 A JP 2011265591A JP 2013117284 A JP2013117284 A JP 2013117284A
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ring
bearing
peripheral
axis
eccentric
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JP2011265591A
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Japanese (ja)
Inventor
Kunihiko Suzuki
邦彦 鈴木
Hiroshi Takuno
博 宅野
Keita Nomura
啓太 野村
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Jtekt Corp
株式会社ジェイテクト
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Priority to JP2011265591A priority Critical patent/JP2013117284A/en
Priority claimed from EP20120194963 external-priority patent/EP2602509B1/en
Publication of JP2013117284A publication Critical patent/JP2013117284A/en
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    • Y02T10/641

Abstract

PROBLEM TO BE SOLVED: To provide a speed reduction mechanism configured to achieve cost reduction and extended life of a bearing therein, and a motor torque transmission device including the same.SOLUTION: In a reduction-transmission mechanism 5, a plurality of output members 53 are arranged at such positions that a size that is the sum of a fitting clearance formed between an outer periphery of each output member and a needle roller bearing 55, a fitting clearance formed between the needle roller bearing 55 and an inner periphery of a plurality of pin insertion holes 50b, and a radial internal clearance in the needle roller bearing 55 is smaller than a size that is the sum of a fitting clearance formed between a ball bearing 54 and an outer periphery of an eccentric portion 42a, a fitting clearance formed between the ball bearing 54 and an inner periphery of a center hole 50a, and a radial internal clearance in the ball bearing 54.

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 speed reduction mechanism.
  A conventional motor rotational force transmission device includes an electric motor that generates a motor rotational force, and a deceleration transmission mechanism that decelerates the motor rotational force of the electric motor and transmits a driving force 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. On the outer peripheral surface of the motor shaft, an eccentric portion having a central axis that is an axis that is eccentric with a predetermined amount of eccentricity is integrally provided.
  The speed reduction transmission mechanism has a pair of speed reduction transmission parts and a housing that houses the pair of speed reduction transmission parts around the axis thereof, and is disposed between the electric motor and the differential mechanism (difference case), and It is connected to the motor shaft and differential case. One deceleration transmission unit is coupled to the motor shaft, and the other deceleration transmission unit is coupled to the differential case.
  With the above configuration, the motor shaft of the electric motor is rotated by the electric power of the vehicle-mounted battery, and accordingly, the motor rotational force is transmitted from the electric motor to the differential mechanism via the speed reduction transmission mechanism. To be distributed.
  By the way, the deceleration transmission part of this type of motor rotational force transmission device includes a pair of disk-shaped revolving members that revolve by rotating the motor shaft of the electric motor, and a plurality of outer pins that impart a revolving force to these revolving members. And a plurality of inner pins for outputting the rotational force of the revolving member as a rotational force to the differential mechanism inside the outer pins.
  The pair of revolving members have a central hole that opens in the direction of the central axis, and a plurality of pin insertion holes that are arranged at equal intervals around the central axis of the central hole. Through a 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, the revolution speed of the external gear, which is a revolution member, becomes relatively high. A load due to centrifugal force is applied to the bearing on the cam side. As a result, it is necessary to use a highly durable bearing as the cam-side bearing, which increases costs. Further, when a load due to centrifugal force is applied to the cam-side bearing, there is a problem that the life of the cam-side bearing is reduced.
  Accordingly, an object of the present invention is to provide a speed reduction mechanism capable of reducing the cost and extending the life of a bearing, and a motor torque transmission device including the speed reduction mechanism.
  In order to achieve the above object, the present invention provides a speed reduction mechanism (1) to (8) and a motor torque transmission device including the speed reduction mechanism.
(1) A rotary shaft that rotates around the first axis and has an eccentric portion having a second axis that is eccentric from the first axis as a central axis, and an outer periphery of the rotary shaft; And a plurality of through holes arranged in parallel at equal intervals around the third axis, and between the inner peripheral surface of the central hole and the outer peripheral surface of the eccentric part. An input member composed of an external gear with a first bearing interposed therein, a rotation force applying member meshed with the input member and composed of an internal gear having a number of teeth larger than the number of teeth of the external gear, A plurality of outputs that receive the rotation force applied to the input member by the rotation force application member and output the rotation force to the output object, and have the second bearing on the outer periphery and pass through the plurality of through holes, respectively. A plurality of output members, the outer peripheral surface and the second output member. The total dimension of the fit clearance formed between the bearing, the fit clearance formed between the second bearing and the inner peripheral surfaces of the plurality of through holes, and the radial internal clearance of the second bearing. S 'is a fit clearance formed between the first bearing and the outer peripheral surface of the eccentric portion, a fit clearance formed between the first bearing and the inner peripheral surface of the center hole, and the A speed reduction mechanism arranged at a position smaller than the total dimension S of the radial internal clearances of the first bearing.
(2) In the speed reduction mechanism according to (1), the first bearing includes an inner ring disposed on an outer periphery of the eccentric portion, an outer ring disposed on an outer periphery of the inner ring, and the outer ring and the inner ring. And D is a dimension obtained by subtracting the outer diameter of the eccentric portion from the inner diameter of the inner ring, and the outer diameter of the outer ring is subtracted from the inner diameter of the center hole. The dimension S is set to one of S = D + d + t, S = d + t, S = D + t, and S = t, where d is the dimension d and t is the operating clearance of the radial internal clearance in the first bearing. Yes.
(3) In the speed reduction mechanism according to (1), the first bearing includes an inner ring raceway surface formed on an outer peripheral surface of the eccentric portion, and an outer ring disposed on an outer periphery of the inner ring raceway surface. And a dimension obtained by subtracting the outer diameter of the outer ring from the inner diameter of the center hole, wherein the first ring includes the rolling element disposed between the outer ring and the inner ring raceway surface. The dimension S is set to S = d + t or S = t, where t is the operating clearance of the radial internal clearance in the bearing.
(4) In the speed reduction mechanism according to (1), the first bearing includes an outer ring raceway surface formed on an inner peripheral surface of the center hole, and is disposed on an inner periphery of the outer ring raceway surface. An inner ring, and a rolling element disposed between the inner ring and the outer ring raceway surface, wherein D is a dimension obtained by subtracting the outer diameter of the eccentric portion from the inner diameter of the inner ring. The dimension S is set to S = D + t or S = t, where t is the operating clearance of the radial internal clearance of the bearing.
(5) In the speed reduction mechanism according to (1), the first bearing includes an inner ring raceway surface formed on an outer peripheral surface of the eccentric portion and an outer ring raceway surface formed on an inner peripheral surface of the center hole. And a rolling element disposed between the outer ring raceway surface and the inner ring raceway surface, and when the operating clearance of the radial internal clearance in the first bearing is t, the dimension S is S = t is set.
(6) In the reduction mechanism according to (1), the second bearing includes an inner ring raceway surface formed on an outer peripheral surface of the output member, and an outer ring disposed on an outer periphery of the inner ring raceway surface. And a fitting gap formed between an outer peripheral surface of the outer ring and inner peripheral surfaces of the plurality of through holes, and a rolling element disposed between the outer ring and the inner ring raceway surface. When S 1 is set and the internal clearance is S 2 , the dimension S ′ is set to S ′ = S 1 + S 2 or S ′ = S 2 .
(7) In the speed reduction mechanism according to (1), the second bearing includes an inner ring disposed on an outer periphery of the output member, an outer ring disposed on an outer periphery of the inner ring, and the outer ring and the inner ring. And a fitting clearance formed between the outer peripheral surface of the output member and the inner peripheral surface of the inner ring is S 0, and the outer peripheral surface of the outer ring is And the internal clearance of the plurality of through-holes is S 1 and the internal clearance is S 2 , the dimension S ′ is S ′ = S 0 + S 1 + S 2 , S '= S 0 + S 2 , S ′ = S 1 + S 2 or S ′ = S 2 is set.
(8) In a motor rotational force transmission device comprising: an electric motor that generates a motor rotational force; and a speed reduction mechanism that decelerates the motor rotational force of the electric motor and outputs a driving force. 1) A motor rotational force transmission device which is the speed reduction mechanism according to any one of 7 to 7.
  According to the present invention, the cost can be reduced and the life of the bearing can be extended.
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 motor rotational force transmission apparatus which concerns on the 1st Embodiment of this invention. FIG. 3 is a cross-sectional view schematically showing the speed reduction mechanism of the motor torque transmission device according to the first embodiment of the present invention. Sectional drawing which shows typically the principal part of the deceleration mechanism in the motor rotational force transmission apparatus which concerns on the 1st Embodiment of this invention. Sectional drawing which shows the support state of the input member with respect to the eccentric part of the deceleration mechanism in the motor rotational force transmission apparatus which concerns on the 1st Embodiment of this invention, and the attachment state of the 2nd bearing with respect to an output member. (A) And (b) is sectional drawing which simplifies and shows the operation state of the input member with respect to the output member of the deceleration mechanism in the motor rotational force transmission apparatus which concerns on the 1st Embodiment of this invention. (A) shows the initial position of the input member, and (b) shows the movement position of the input member. (A) And (b) is sectional drawing which simplifies and shows the operation state of the outer ring of the 2nd bearing with respect to the output member of the deceleration mechanism in the motor rotational force transmission apparatus which concerns on the 1st Embodiment of this invention. (A) shows the initial position of the outer ring, and (b) shows the movement position of the outer ring. (A) And (b) is sectional drawing which simplifies and shows the operation state of the input member with respect to the eccentric part of the deceleration mechanism in the motor rotational force transmission apparatus which concerns on the 1st Embodiment of this invention. (A) shows the initial position of the input member, and (b) shows the movement position of the input member. Sectional drawing which simplifies and shows the support state of the input member with respect to the eccentric part of the deceleration mechanism in the motor rotational force transmission apparatus which concerns on the 2nd Embodiment of this invention, and the attachment state of the 2nd bearing with respect to an output member. Sectional drawing which simplifies and shows the support state of the input member with respect to the eccentric part of the deceleration mechanism in the motor rotational force transmission apparatus which concerns on the 3rd Embodiment of this invention, and the attachment state of the 2nd bearing with respect to an output member. Sectional drawing which simplifies and shows the support state of the input member with respect to the eccentric part of the deceleration mechanism in the motor rotational force transmission apparatus which concerns on the 4th Embodiment of this invention, and the attachment state of the 2nd bearing with respect to an output member. In the motor rotational force transmission apparatus according to the first embodiment of the present invention, the support state of the input member with respect to the eccentric portion of the speed reduction mechanism and the mounting state of the second bearing with respect to the output member are simplified and modified example (1). FIG. Modified example (2) in which the support state of the input member with respect to the eccentric portion of the speed reduction mechanism and the attachment state of the second bearing with respect to the output member are simplified in the motor torque transmission device according to the second embodiment of the present invention. FIG. Modified example (3) in which the support state of the input member relative to the eccentric portion of the speed reduction mechanism and the attachment state of the second bearing relative to the output member are simplified in the motor torque transmission device according to the third embodiment of the present invention. FIG. Modified example (4) in which the support state of the input member with respect to the eccentric portion of the speed reduction mechanism and the attachment state of the second bearing with respect to the output member are simplified in the motor torque transmission device according to the fourth embodiment of the present invention. FIG.
[First embodiment]
Hereinafter, a motor torque transmission device according to a first embodiment of the present invention 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 is configured to transmit a driving force based on the motor rotational force of the electric motor 4 (described later) to the pair of rear wheels 105. Thereby, the motor rotational force of the electric motor 4 is output to the rear axle shaft 106 via the deceleration transmission mechanism 5 and the rear differential 3 (both will be 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 via the transaxle 103, and the pair of front wheels 104 are driven.
(Whole structure of the motor rotational force 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 a central axis that is an axis of the rear axle shaft 106 (shown in FIG. 1) (rotational axis O 1 as the first axis), and a pair of rear The rear differential 3 as a driving force transmission target for distributing the driving force to the wheels 105 (shown in FIG. 1), the electric motor 4 for generating the motor rotational force for operating the rear differential 3, and the motor rotation of the electric motor 4 It is generally composed of a deceleration transmission mechanism 5 that decelerates the force and transmits the driving force 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 of the housing 2 (left 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 20 a through which the rear axle shaft 106 (shown in FIG. 1) is inserted is provided at the bottom of the first housing element 20. 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 rotation axis O 1 as a 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.
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 rotation axis O 1 . 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 smaller than the maximum outer diameter of the second housing element 21 and has an outer diameter substantially the same as the outer diameter of the convex portion 23, and has a rotational axis O 1 as a central axis. It is formed with.
  The third housing element 22 is disposed on the other side of the housing 2 (the right side in FIG. 2), and is entirely formed by 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.
(Configuration of rear differential 3)
The rear differential 3 includes a bevel gear type differential mechanism having a differential case (output target) 30, a pinion gear shaft 31, a pair of pinion gears 32, and a pair of side gears 33, and is disposed on one side of the motor rotational force transmission device 1. .
  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 further 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 rotation axis (sixth axis) O 6 , and the ball housing 35 is disposed on the first housing element 20 via the ball bearing 34 and the motor shaft (rotation shaft) 42 of the electric motor 4. It is rotatably supported through The differential case 30 is configured to receive a driving force based on the motor rotational force of the electric motor 4 from the deceleration transmission mechanism 5 and rotate around the rotation axis O 6 .
  The differential case 30 has 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 through which the left and right rear axle shafts 106 are respectively inserted. Is provided.
The differential case 30 is integrally provided with an annular flange 30 c that faces the speed reduction transmission mechanism 5. The flange 30c, pin mounting hole 300c of a plurality (six in this embodiment) in parallel at equal intervals around the rotation axis O 6 is provided.
The pinion gear shaft 31 is disposed on the axis L perpendicular to the rotation axis O 6 in the accommodation space 30 a of the differential case 30, and rotation around the axis L and movement in the axis L direction are restricted by the pin 36.
  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 have shaft connecting holes 33a for connecting the left and right rear axle shafts 106 (shown in FIG. 1) by spline fitting, and are accommodated in the accommodating space 30a of the differential case 30. The pair of side gears 33 are configured to 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)
Electric motor 4, the stator 40 has a rotor 41 and motor shaft 42, it is connected via a reduction transmission mechanism 5 to the rear differential 3 on the rotation axis O 1, and stator 40 ECU (Electronic Control Unit: shown Connected). The electric motor 4 generates a motor rotational force for the stator 40 to input a control signal from the ECU and operate the rear differential 3 between the rotor 41 and the rotor 41 to rotate together with the motor shaft 42. It is configured.
  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 is disposed on the rotation axis O 1 , and 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 third housing element. 22 is rotatably supported via ball bearings 46 on the inner peripheral surface, and the whole is formed by a cylindrical shaft member through which a rear axle shaft 106 (shown in FIG. 1) is inserted.
The one side end portion of the motor shaft 42, flat circular eccentric portion 42a having a center axis corresponding to the axis (second axis) O 2 eccentrically with a eccentricity [delta] 1 from the rotation axis O 1, and the rotation axis O eccentricity δ 2 (δ 1 = δ 2 = δ) axis eccentrically with a (second axis) O'2 flat circular eccentric portion 42b having a center axis corresponding to the is provided integrally from 1. 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 °) around the rotation axis O 1. That is, the one eccentric portion 42a and the other of the eccentric portion 42b, equal to the distance from the distance and the axis O'2 from the axis O 2 to the rotation axis O 1 to the rotation axis O 1, and the axis O 2 and the axis The motor shaft 42 is arranged on the outer periphery so that the distance between the O ′ 2 and the rotation axis O 1 is equal. Further, the eccentric portion 42a and the eccentric portion 42b is disposed in a position parallel along the direction of the rotation axis O 1.
  At the other end of the motor shaft 42, a resolver 47 is disposed as a rotation angle detector interposed between the outer peripheral surface and the inner peripheral surface of the cylindrical portion 22b. 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)
3 and 4 show a deceleration transmission mechanism. 5A and 5B show the support state of the input member and the attachment state of the second bearing. As shown in FIGS. 3 and 4, the speed reduction transmission mechanism 5 includes a pair of input members 50, 51, a rotation force applying member 52, and a plurality (six in this embodiment) of output members 53, and the rear differential 3 And the electric motor 4 (both shown in FIG. 2). The deceleration transmission mechanism 5 is configured to decelerate the motor rotational force of the electric motor 4 and transmit the driving force to the rear differential 3 as described above.
As shown in FIG. 4, one input member 50 is formed of an external gear having a center hole 50a having an axis (third axis) O 3 as a center axis, and the rear differential 3 (FIG. 2) and a ball bearing 54 as a first bearing is interposed between the inner peripheral surface of the center hole 50a and the eccentric portion 42a so as to be rotatably supported by the motor shaft 42. One input member 50 receives a motor rotational force from the electric motor 4 and performs a circular motion in the directions of arrows m 1 and m 2 (shown in FIG. 3) having an eccentricity δ (revolving motion about the rotation axis O 1 ). Is configured to do. The ball bearing 54 includes an inner ring 540 and an outer ring 541 as two races arranged inside and outside thereof, and a rolling element 542 that rolls between the inner ring 540 and the outer ring 541. The inner ring 540 is attached to the eccentric portion 42a, and the outer ring 541 is attached to the center hole 50a with a gap (gap) in the radial direction of the motor shaft 42, respectively. That is, the inner ring 540 is attached to the outer peripheral surface of the eccentric portion 42a, and the outer ring 541 is attached to the inner peripheral surface of the center hole 50a by clearance fitting. In FIG. 4, showing a state where the centrifugal force P 1 is applied to one input member 50, an inner ring 540, outer ring 541 and the rolling elements 542.
On one of the input member 50, the pin insertion hole (through hole) 50b of the plurality (six in this embodiment) in parallel at equal intervals in the axial line O 3 about is provided. The hole diameter of the pin insertion hole 50b is set to be larger than the dimension obtained by adding the outer diameter of the needle roller bearing 55 as the second bearing to the outer diameter of the output member 53. The outer diameter of the needle roller bearing 55 is set to be smaller than the outer diameter of the ball bearing 54. On the outer peripheral surface of one input member 50, external teeth 50c having an involute tooth profile are provided.
The external teeth 50c have both tooth surfaces (both circumferential tooth surfaces of the input member 50) with respect to both tooth surfaces of the internal teeth 52c of the rotational force applying member 52 (both circumferential tooth surfaces of the rotating force applying member 52). It is comprised so that it may function as a revolution force provision surface and a rotation force receiving surface. Number of teeth Z 1 of the external teeth 50c is set to, for example, Z 1 = 195.
As shown in FIG. 4, the other input member 51 includes an external gear having a center hole 51 a having an axis (third axis) O ′ 3 as a center axis, and the electric motor 4 ( 2) and is rotatably supported by the motor shaft 42 with a ball bearing 56 as a first bearing interposed between the inner peripheral surface of the center hole 51a and the eccentric portion 42b. . The other input member 51 receives a motor rotational force from the electric motor 4 and performs a circular motion in the directions of arrows m 1 and m 2 (shown in FIG. 3) having an eccentricity δ (revolving motion around the rotation axis O 1 ). Is configured to do. The ball bearing 56 includes an inner ring 560 and an outer ring 561 as two races arranged inside and outside thereof, and a rolling element 562 that rolls between the inner ring 560 and the outer ring 561. The inner ring 560 is attached to the eccentric portion 42b, and the outer ring 561 is attached to the center hole 51a with a gap (gap) in the radial direction of the motor shaft 42, respectively. That is, the inner ring 560 is attached to the outer peripheral surface of the eccentric portion 42b, and the outer ring 561 is attached to the inner peripheral surface of the center hole 51a by clearance fitting. In FIG. 4, showing the other of the input member 51, an inner ring 560, a state where the centrifugal force P 2 is applied to the outer ring 561 and the rolling elements 562.
To the other input member 51, the pin insertion hole (through hole) 51b of the plurality (six in this embodiment) in parallel at equal intervals in the axial O'3 about is provided. The hole diameter of the pin insertion hole 51b is set to be larger than the dimension obtained by adding the outer diameter of the needle roller bearing 57 as the second bearing to the outer diameter of the output member 53. The outer diameter of the needle roller bearing 57 is set to be smaller than the outer diameter of the ball bearing 56. An outer tooth 51 c having an involute tooth profile is provided on the outer peripheral surface of the other input member 51.
The external teeth 51 c have both tooth surfaces (both circumferential tooth surfaces of the input member 51) with respect to both tooth surfaces of the internal teeth 52 c in the rotational force applying member 52 (both circumferential tooth surfaces of the rotating force applying member 52). It is comprised so that it may function as a revolution force provision surface and a rotation force receiving surface. 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 an internal gear having the rotation axis O 1 as a central axis, and is disposed between the first housing element 20 and the second housing element 21. 1 is formed by a bottomless cylindrical member that opens in both directions 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. and it is also configured other input member 51 to the arrow l 1, l 2 direction of rotation force so as to give respectively.
A first fitting portion 52 a fitted to the outer peripheral surface of the convex portion 23 and a second fitting portion 52 b fitted to the outer peripheral surface of the convex portion 27 rotate on the inner peripheral surface of the rotation force applying member 52. They are provided at a predetermined interval in the direction of the axis O 1 . Further, the external teeth 50c of one input member 50 and the other input member are interposed on the inner peripheral surface of the rotation force applying member 52 between the first fitting portion 52a and the second fitting portion 52b. An involute tooth-shaped inner tooth 52 c that meshes with the outer tooth 51 c of 51 is provided. Number of teeth Z 3 of the internal teeth 52c is set to, for example, Z 3 = 208. Thereby, the reduction ratio α of the deceleration transmission mechanism 5 is calculated from α = (Z 3 −Z 2 ) / Z 2 .
  6A and 6B show the fitting clearance of the second bearing. FIGS. 7A and 7B show the operating clearance of the radial internal clearance of the second bearing. FIGS. 8 (a) and 8 (b) show the operating clearance of the fitting clearance and radial internal clearance of the first bearing. As shown in FIGS. 2 and 6 to 8, the plurality of output members 53 include a bolt having a screw portion 53 a at one end and a head 53 b at the other end, and one input member The threaded portion 53a is attached to the pin attachment hole 300c of the differential case 30 through the pin insertion hole 50b of 50 and the pin insertion hole 51b of the other input member 51.
Further, the plurality of output members 53 are inserted through an annular spacer 58 interposed between the head 53b and the other input member 51, and the fitting clearances S of the needle roller bearings 55 and 57 with respect to the input members 50 and 51 are inserted. 0 (S 0 = 0 in the present embodiment), S 1 and the radial internal clearance S 2 (S 2 = w: operating clearance), the total dimension S ′ (not shown) is the input member of the ball bearings 54, 56. Dimensions S (S = S 3 + S 4 + S 5 > S 0 + S) obtained by adding together the fitting clearances S 3 and S 4 (both not shown) and radial internal clearance S 5 (S 5 = t: operating clearance) for 50 and 51 1 + S 2 = S ′). As a result, when the input members 50 and 51 receive loads due to the centrifugal forces P 1 and P 2 generated based on the circular motion and move in the direction, the inner peripheral surfaces of the center holes 50 a and 51 a cause the ball bearings 54 and 56 to move. The inner peripheral surfaces of the pin insertion holes 50b and 51b contact the outer peripheral surface of the output member 53 via the needle roller bearings 55 and 57 before contacting the outer peripheral surfaces of the eccentric parts 42a and 42b.
The fitting clearance S 0 is between the outer peripheral surface of the output member 53 and the inner peripheral surface of the inner ring of the needle roller bearing 55, and between the outer peripheral surface of the output member 53 and the inner peripheral surface of the inner ring of the needle roller bearing 57. Formed between.
Clearance S 1 fit in the inner peripheral surface of the outer peripheral surface the pin insertion hole 50b of a space between the inner circumferential surface of the outer peripheral surface and the pin insertion hole 50b of the outer ring 550 of the needle roller bearing 55 the outer race 550, also the needle Between the outer peripheral surface of the outer ring 570 of the tapered roller bearing 57 and the inner peripheral surface of the pin insertion hole 51b, the outer peripheral surface of the outer ring 570 is formed at a position closest to the inner peripheral surface of the pin insertion hole 51b.
Clearance S 3 fit is between the outer peripheral surface of the outer ring 541 of the inner peripheral surface of the center hole 50a and the ball bearing 54, also between the outer peripheral surface of the outer ring 561 of the inner peripheral surface of the center hole 51a and the ball bearing 56 Is formed.
Clearance S 4 fit is provided between the inner peripheral surface and the outer peripheral surface of the eccentric portion 42a of the inner race 540 of the ball bearing 54, also between the inner circumferential surface and the outer peripheral surface of the eccentric portion 42b of the inner ring 560 of the ball bearing 56 Is formed.
  The plurality of output members 53 are configured to 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.
  A contact resistance between the outer peripheral surfaces of the plurality of output members 53 and the inner peripheral surface of the pin insertion hole 50b in one input member 50 is provided at a portion interposed between the screw portion 53a and the head portion 53b. Needle roller bearings 55 for reducing and needle roller bearings 57 for reducing contact resistance with the inner peripheral surface of the pin insertion hole 51b in the other input member 51 are attached.
  The needle roller bearing 55 includes an inner ring raceway surface on the outer peripheral surface of the output member 53, and a race (outer ring) 550 that can contact the inner peripheral surfaces of the plurality of pin insertion holes 50b in one input member 50, and the race. Needle rollers 551 that roll between the inner peripheral surface of 550 and the inner ring raceway surface of the output member 53 are provided. The needle roller bearing 57 includes a race (outer ring) 570 that includes an inner ring raceway surface on the outer peripheral surface of the output member 53 and that can contact the inner peripheral surfaces of the plurality of pin insertion holes 51b in the other input member 51, and this race. Needle rollers 571 that roll between the inner peripheral surface of 570 and the inner ring raceway surface of the output member 53 are provided.
Here, the fitting clearance S 0 + S 1 (S 0 + S 1 = S 1 because S 0 = 0 in this embodiment), the internal clearance of the second bearing (needle roller bearings 55 and 57). S 2 and dimension S (S = S 3 + S 4 + S 5 ) will be described separately on one input member 50 side and the other input member 51 side.
In one of the input member 50 side, the gap S 1 fitting, as shown in FIG. 6 (a) and (b), the output member 53 is its initial position (position shown in FIG. 6 (a)) from the axis (5 closest located on the inner peripheral surface of the pin insertion hole 50b relative movement between the axis) O 5 with the axis (fourth axis) O 4 and the input member 50 in the state of being matched outer ring 550 of ( The dimension (S 1 = 2 × (s 1 −s ′ 1 )) that is twice the dimension up to the position shown in FIG. 6B is set. In the initial position, the output member 53 is in a pin insertion hole in a state where the axis O 5 and the axis O 4 are aligned with the rotation axis O 6 and the rotation axis O 1 , and the axis O 2 and the axis O 3 are aligned with each other. 50b is disposed on one side of the opening surface (in FIG. 6A, on the opening surface upper side).
Internal clearance S 2, as shown in FIG. 7 (a) and (b), the outer ring 550 of the needle roller bearing 55 is fitted to the axis (fifth axis) O 5 of the output member 53 to the axis O 4 Dimensions from the position (initial position shown in FIG. 7A) to the output member 53 in the radial direction (first direction X 1 ) and the closest position (moving position shown in FIG. 7B) Is set to a dimension (S 2 = 2 × (s 2 −s ′ 2 )). As shown in FIG. 5, when the dimension (R 1 -R 3 ) from the initial position to the moving position of the outer ring 550 is used, S 2 = 2 × (R 1 -R 3 ). In this case, the internal clearance S 2 is the operating clearance w of the needle roller bearing 55. The dimension R 1 is a dimension from the axis O 6 to the outer peripheral surface of the outer ring 550 (the part farthest from the axis O 6 ) at the initial position of the outer ring 550. Dimension R 2, in the movement position of the outer ring 550 is the dimension from the axis O 6 to the outer peripheral surface of the outer ring 550 (the farthest portion from the axis O 6).
As shown in FIGS. 8A and 8B, the dimension S is an eccentric portion from the position where one input member 50 makes the axis O 3 coincide with the axis O 2 (the initial position shown in FIG. 8A). A dimension (S = 2 × (s−s ′) obtained by doubling the dimension up to the position closest to the position 42a in the radial direction (second direction X 2 ) (the movement position shown in FIG. 8B). )) Is set. In this case, as shown in FIG. 5, the dimension obtained by subtracting the outer diameter of the eccentric portion 42a from the inner diameter of the inner ring 540 is D, and the dimension obtained by subtracting the outer diameter of the outer ring 541 from the inner diameter of the center hole 50a is d. When the operation clearance of the radial internal clearance in the ball bearing 54 is t, the dimension S is S = D + d + t.
Similarly, the other of the input member 51 side, the gap S 1 fitting the axial line from FIG. 6 (a) and as shown in (b), (the position shown in FIG. 6 (a)) the output member 53 is its initial position In the state where O 5 and the axis (fourth axis) O ′ 4 of the outer ring 570 coincide with each other, the position moves relative to the input member 51 and is closest to the inner peripheral surface of the pin insertion hole 51b (FIG. 6). It is set to a dimension (S 1 = 2 × (s 1 −s ′ 1 )) that is twice the dimension up to the position shown in (b). In the initial position, the output member 53 is in a state where the axis O 5 and the axis O ′ 4 are aligned with the rotation axis O 6 and the rotation axis O 1 , and the axis O ′ 2 and the axis O ′ 3 are aligned with each other. The pin insertion hole 51b is disposed on one side of the opening surface (in FIG. 6A, on the opening surface upper side).
Internal clearance S 2, as shown in FIG. 7 (a) and (b), so the outer ring 570 of the needle roller bearing 57 coincides with the axis (fifth axis) O 5 of the output member 53 the axis O'4 From the position (initial position shown in FIG. 7A) to the output member 53 in the radial direction (first direction X 1 ) and the closest position (movement position shown in FIG. 7B). It is set to a dimension (S 2 = 2 × (s 2 −s ′ 2 )) that is twice the dimension. As shown in FIG. 5, when the dimension (R 4 −R 2 ) from the initial position to the moving position of the outer ring 570 is used, S 2 = 2 × (R 4 −R 2 ). In this case, the internal clearance S 2 becomes the operating clearance w ′ of the needle roller bearing 57. The dimension R 4 is a dimension from the axis O 6 to the outer peripheral surface of the outer ring 570 (the part farthest from the axis O 6 ) at the initial position of the outer ring 570. Dimension R 2, in the movement position of the outer ring 570 is the dimension from the axis O 6 to the outer peripheral surface of the outer ring 570 (the farthest portion from the axis O 6).
As shown in FIGS. 8A and 8B, the dimension S is determined from the position where the other input member 51 matches the axis O ′ 3 with the axis O ′ 2 (the initial position shown in FIG. 8A). A dimension (S = 2 × (s−) that doubles the dimension to the position closest to the eccentric part 42b in the radial direction (second direction X 2 ) and the closest position (the movement position shown in FIG. 8B). s')). In this case, as shown in FIG. 5, the dimension obtained by subtracting the outer diameter of the eccentric portion 42b from the inner diameter of the inner ring 560 is D ′, and the dimension obtained by subtracting the outer diameter of the outer ring 561 from the inner diameter of the center hole 51a is d ′. When the operating clearance of the radial internal clearance in the ball bearing 56 is t ′, the dimension S is S = D ′ + d ′ + t ′.
(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, this motor rotational force is applied to the deceleration transmission mechanism 5 via the motor shaft 42, and 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, about the axis O 3 while meshing with the internal teeth 52c of the rotation force applying member 52 is the input member 50 of the outer teeth 50c (arrow n 1 direction shown in FIG. 3), also the input member 51 outer teeth 51c the rotates each about the axis O'3 while meshing with the internal teeth 52c of the rotation force applying member 52 (arrow l 1 direction shown in FIG. 3). In this case, due to the rotation of the input members 50 and 51, the inner peripheral surface of the pin insertion hole 50b is in the race 550 of the needle roller bearing 55, and the inner peripheral surface of the pin insertion hole 51b is in the race 570 of the needle roller bearing 57, respectively. Abut.
  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 from the input members 50 and 51 is applied to the differential case 30 as the rotational force. Is output.
  As a result, the 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.
Here, in the motor rotational force transmission device 1, the centrifugal force P 1 is applied to the input member 50 based on the circular motion and the centrifugal force P 2 is applied to the input member 51 based on the circular motion. .
Accordingly, the input member 50 in the direction of action of the centrifugal force P 1 (e.g., the lower part of FIG. 5), also the input member 51 respectively move in the direction of action of the centrifugal force P 2 (e.g., upward in FIG. 5).
In this case, as shown in FIGS. 4 and 5, when one of the input member 50 is under load due to the centrifugal force P 1 generated based on the circular movement to move in that direction, the inner peripheral surface of the center hole 50a is a ball Before contacting the outer peripheral surface of the eccentric portion 42 a via the bearing 54, the inner peripheral surface of the pin insertion hole 50 b contacts the outer peripheral surface of the output member 53 via the needle roller bearing 55. Thereby, the one of the plurality of needle roller bearings 55 by dispersing loads due to centrifugal force P 1 from the input member 50 is subjected. Therefore, load caused by the centrifugal force P 1 from one of the input member 50 is prevented from acting on the ball bearing 54.
Similarly, as shown in FIGS. 4 and 5, when the other input member 51 receives a load due to the centrifugal force P 2 generated on the basis of the circular motion to move in that direction, the inner peripheral surface of the center hole 51a is a ball Before contacting the outer peripheral surface of the eccentric portion 42 b via the bearing 56, the inner peripheral surface of the pin insertion hole 51 b contacts the outer peripheral surface of the output member 53 via the needle roller bearing 57. Thereby, the dispersing the load due to the centrifugal force P 2 from the other input member 51 a plurality of needle roller bearings 57 is subjected. Therefore, it is prevented that the load caused by the centrifugal force P 2 from the other input member 51 acts on the ball bearing 56.
  Therefore, in the present embodiment, it is not necessary to use highly durable bearings for the ball bearings 54 and 56.
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 it is not necessary to use highly durable bearings for the ball bearings 54 and 56, the cost can be reduced.
(2) It is possible to prevent the loads caused by the centrifugal forces P 1 and P 2 from acting on the ball bearings 54 and 56, thereby extending the life of the ball bearings 54 and 56.
In the present embodiment, the case where the dimension S ′ is set to S ′ = S 1 + S 2 has been described. However, the present invention is not limited to this, and the dimension S ′ is set to S ′ = S 2. There is no problem.
[Second Embodiment]
Next, a speed reduction mechanism in a motor torque transmission device according to a second embodiment of the present invention will be described with reference to FIG. FIG. 9 shows the support state of the input member and the attachment state of the second bearing. 9, members having the same or equivalent functions as those in FIG. 5 are denoted by the same reference numerals, and detailed description thereof is omitted.
  As shown in FIG. 9, in the speed reduction transmission mechanism 100 according to the second embodiment of the present invention (partially shown), the inner rings 540, 560 of the ball bearings 54, 56 are arranged on the outer peripheral surfaces of the eccentric portions 42a, 42b. It is characterized in that the outer rings 541 and 561 are attached to the inner peripheral surfaces of the center holes 50a and 51a by clearance fit, respectively, by interference fit.
  Therefore, on the one input member 50 side, when the dimension obtained by subtracting the outer diameter of the outer ring 541 from the inner diameter of the center hole 50a is d, and the operating clearance of the radial internal clearance in the ball bearing 54 is t, the dimension S ( (Shown in FIG. 8) is set to S = d + t.
Further, assuming that the operation clearance of the radial internal clearance in the needle roller receiver 55 is w, the internal clearance S 2 (shown in FIG. 7) is set to S 2 = w.
  Similarly, on the other input member 51 side, when the dimension obtained by subtracting the outer diameter of the outer ring 561 from the inner diameter of the center hole 51a is d ′, and the operating clearance of the radial internal clearance in the ball bearing 56 is t ′, the dimension S is set to S = d ′ + t ′.
Further, assuming that the operation clearance of the radial internal clearance in the needle roller receiver 57 is w ′, the internal clearance S 2 is set to S 2 = w ′.
In the speed reduction transmission mechanism 100 configured as described above, when one input member 50 receives a load due to the centrifugal force P 1 generated based on the circular motion and moves in the direction, the centrifugal force from the one input member 50. dispersing the load applied by P 1 so that the plurality of needle roller bearings 55 is subjected.
Further, when the other input member 51 receives a load due to the centrifugal force P 2 generated based on the circular motion and moves in the direction, the load due to the centrifugal force P 2 from the other input member 51 is dispersed to thereby disperse a plurality of needles. The tapered roller bearing 57 is received.
Therefore, in the present embodiment, as in the first embodiment, the load caused by the centrifugal force P 1 from one input member 50 is applied to the ball bearing 54 and the centrifugal force P 2 from the other input member 51. Is prevented from acting on the ball bearings 56, and it is not necessary to use highly durable bearings for the ball bearings 54 and 56.
[Effect of the second embodiment]
According to the second embodiment described above, the same effects as those shown in the first embodiment can be obtained.
  In the present embodiment, the inner ring 540 disposed around the outer periphery of the eccentric portion 42a, the outer ring 541 disposed around the outer periphery of the inner ring 540, and the outer ring 541 and the inner ring 540 are disposed. A ball bearing 54 formed of a rolling element 542 is also disposed between an inner ring 560 disposed on the outer periphery of the eccentric portion 42b, an outer ring 561 disposed on the outer periphery of the inner ring 560, and between the outer ring 561 and the inner ring 560. In the above description, the ball bearings 56 made of the rolling elements 562 are used as the first bearings. However, the present invention is not limited to this, and includes an inner ring raceway surface formed on the outer peripheral surface of the eccentric portion. In addition, a ball bearing including an outer ring disposed on the outer periphery of the inner ring raceway surface and a rolling element disposed between the outer ring and the inner ring raceway surface may be used as the first bearing. In this case, when the outer ring is attached to the inner peripheral surface of the center hole by clearance fitting, the dimension S is set to S = d + t, d ′ + t ′ as shown in the above embodiment. On the other hand, when the outer ring is attached to the inner peripheral surface of the center hole by an interference fit, the dimension S is set to S = t, t ′.
In this embodiment, the case where the dimension S ′ is set to S ′ = S 1 + S 2 has been described. However, the present invention is not limited to this, and the dimension S ′ is set to S ′ = S 2. There is no problem.
[Third embodiment]
Next, a speed reduction mechanism in a motor torque transmission device according to a third embodiment of the present invention will be described with reference to FIG. FIG. 10 shows the support state of the input member and the attachment state of the second bearing. 10, members having the same or equivalent functions as those in FIG. 5 are denoted by the same reference numerals, and detailed description thereof is omitted.
  As shown in FIG. 10, in the speed reduction transmission mechanism 200 (partially shown) according to the third embodiment of the present invention, the inner rings 540, 560 of the ball bearings 54, 56 are arranged on the outer peripheral surfaces of the eccentric portions 42a, 42b. It is characterized in that the outer rings 541 and 561 are attached to the inner peripheral surfaces of the center holes 50a and 51a by interference fit, respectively, by clearance fit.
  Therefore, on the one input member 50 side, when the dimension obtained by subtracting the outer diameter of the eccentric portion 42a from the inner diameter of the inner ring 540 is D, and the operating clearance of the radial internal clearance in the ball bearing 54 is t, the dimension S ( (Shown in FIG. 8) is set to S = D + t.
Further, assuming that the operation clearance of the radial internal clearance in the needle roller receiver 55 is w, the internal clearance S 2 (shown in FIG. 7) is set to S 2 = w.
  Similarly, on the other input member 51 side, when the dimension obtained by subtracting the outer diameter of the eccentric portion 42b from the inner diameter of the inner ring 560 is D ′ and the operating clearance of the radial internal clearance in the ball bearing 56 is t ′, the dimension S is set to S = D ′ + t ′.
Further, assuming that the operation clearance of the radial internal clearance in the needle roller receiver 57 is w ′, the internal clearance S 2 is set to S 2 = w ′.
In the speed reduction transmission mechanism 200 configured as described above, when one input member 50 receives a load due to the centrifugal force P 1 generated based on the circular motion and moves in the direction, the centrifugal force from the one input member 50. dispersing the load applied by P 1 so that the plurality of needle roller bearings 55 is subjected.
Further, when the other input member 51 receives a load due to the centrifugal force P 2 generated based on the circular motion and moves in the direction, the load due to the centrifugal force P 2 from the other input member 51 is dispersed to thereby disperse a plurality of needles. The tapered roller bearing 57 is received.
Therefore, in the present embodiment, as in the first embodiment, the load caused by the centrifugal force P 1 from one input member 50 is applied to the ball bearing 54 and the centrifugal force P 2 from the other input member 51. Is prevented from acting on the ball bearings 56, and it is not necessary to use highly durable bearings for the ball bearings 54 and 56.
[Effect of the third embodiment]
According to the third embodiment described above, the same effects as those shown in the first embodiment can be obtained.
  In the present embodiment, the inner ring 540 disposed around the outer periphery of the eccentric portion 42a, the outer ring 541 disposed around the outer periphery of the inner ring 540, and the outer ring 541 and the inner ring 540 are disposed. A ball bearing 54 formed of a rolling element 542 is also disposed between an inner ring 560 disposed on the outer periphery of the eccentric portion 42b, an outer ring 561 disposed on the outer periphery of the inner ring 560, and between the outer ring 561 and the inner ring 560. However, the present invention is not limited to this, and the outer ring raceway surface formed on the inner peripheral surface of the center hole is used. In addition, a ball bearing including an inner ring disposed on the inner periphery of the outer ring raceway surface and a rolling element disposed between the inner ring and the outer ring raceway surface may be used as the first bearing. In this case, when the inner ring is attached to the outer peripheral surface of the eccentric portion by clearance fitting, the dimension S is set to S = D + t, D ′ + t ′ as shown in the above embodiment. On the other hand, when the inner ring is attached to the outer peripheral surface of the eccentric portion by interference fit, the dimension S is set to S = t, t ′.
In this embodiment, the case where the dimension S ′ is set to S ′ = S 1 + S 2 has been described. However, the present invention is not limited to this, and the dimension S ′ is set to S ′ = S 2. There is no problem.
[Fourth embodiment]
Next, a speed reduction mechanism in a motor torque transmission device according to a fourth embodiment of the present invention will be described with reference to FIG. FIG. 11 shows the support state of the input member and the attachment state of the second bearing. 11, members having the same or equivalent functions as those in FIG. 5 are denoted by the same reference numerals, and detailed description thereof is omitted.
  As shown in FIG. 11, in the speed reduction transmission mechanism 300 (partially shown) according to the fourth embodiment of the present invention, the inner rings 540 and 560 of the ball bearings 54 and 56 are arranged on the outer peripheral surfaces of the eccentric portions 42 a and 42 b. In addition, the outer rings 541 and 561 are characterized in that they are attached to the inner peripheral surfaces of the center holes 50a and 51a by an interference fit, respectively.
  For this reason, on one input member 50 side, if the operation clearance of the radial internal clearance in the ball bearing 54 is t, the dimension S (shown in FIG. 8) is set to S = t.
Further, assuming that the operation clearance of the radial internal clearance in the needle roller receiver 55 is w, the internal clearance S 2 (shown in FIG. 7) is set to S 2 = w.
  Similarly, on the other input member 51 side, when the operation clearance of the radial internal clearance in the ball bearing 56 is t ′, the dimension S is set to S = t ′.
Further, assuming that the operation clearance of the radial internal clearance in the needle roller receiver 57 is w ′, the internal clearance S 2 is set to S 2 = w ′.
This in reduction transmission mechanism 300 configured as described above, one of the input member 50 is under load due to the centrifugal force P 1 generated based on the circular movement to move in that direction, the centrifugal force from one input member 50 dispersing the load applied by P 1 so that the plurality of needle roller bearings 55 is subjected.
Further, when the other input member 51 receives a load due to the centrifugal force P 2 generated based on the circular motion and moves in the direction, the load due to the centrifugal force P 2 from the other input member 51 is dispersed to thereby disperse a plurality of needles. The tapered roller bearing 57 is received.
Therefore, in the present embodiment, as in the first embodiment, the load caused by the centrifugal force P 1 from one input member 50 is applied to the ball bearing 54 and the centrifugal force P 2 from the other input member 51. Is prevented from acting on the ball bearings 56, and it is not necessary to use highly durable bearings for the ball bearings 54 and 56.
[Effect of the fourth embodiment]
According to the fourth embodiment described above, the same effects as those shown in the first embodiment can be obtained.
  In the present embodiment, the inner ring 540 disposed around the outer periphery of the eccentric portion 42a, the outer ring 541 disposed around the outer periphery of the inner ring 540, and the outer ring 541 and the inner ring 540 are disposed. A ball bearing 54 formed of a rolling element 542 is also disposed between an inner ring 560 disposed on the outer periphery of the eccentric portion 42b, an outer ring 561 disposed on the outer periphery of the inner ring 560, and between the outer ring 561 and the inner ring 560. Although the case where the ball bearings 56 made of the rolling elements 562 are used as the first bearings has been described, the present invention is not limited to this, and the inner ring raceway surface formed on the outer peripheral surface of the output member, and A ball bearing that includes an outer ring raceway surface formed on the inner peripheral surface of the center hole and that includes a rolling element disposed between the outer ring raceway surface and the inner ring raceway surface may be used as the first bearing. .
In this embodiment, the case where the dimension S ′ is set to S ′ = S 1 + S 2 has been described. However, the present invention is not limited to this, and the dimension S ′ is set to S ′ = S 2. There is no problem.
  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, equal to the distance from the distance and the axis O'2 from the axis O 2 to the rotation axis O 1 to the rotation axis O 1, and between the axis O 2 and the axis O'2 One eccentric portion 42a and the other eccentric portion 42b are provided on the outer peripheral surface of the motor shaft 42 so as to equalize the distances around the rotation axis O, and the axis (rotation axis) of the motor shaft 42 of the electric motor 4 is provided. Although the case where the pair of input members 50 and 51 are arranged at the portions spaced apart at equal intervals (180 °) around O 1 ) has been described, the present invention is not limited to this, and the number of input members is appropriately determined. Can be changed.
  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. Arranged on the outer periphery of the motor shaft, n input members are arranged on the motor shaft at portions spaced apart by 360 ° / n around the axis.
  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 of two eccentric parts adjacent to each other and the axis of the motor shaft is 120 °, and three inputs The members are arranged on the motor shaft at portions spaced apart by 120 ° around the axis.
(2) In the above embodiment, the case where the needle roller bearings 55 and 57 as the second bearings are composed of the outer rings 550 and 570 and the needle rollers 551 and 571 has been described, but the present invention is not limited to this. Further, the present invention may be a needle roller bearing comprising an inner ring disposed around the outer periphery of the output member, an outer ring disposed around the outer periphery of the inner ring, and a needle roller disposed between the outer ring and the inner ring. . In this case, the dimension S ′ is set to one of S ′ = S 0 + S 1 + S 2 , S ′ = S 0 + S 2 , S ′ = S 1 + S 2 and S ′ = S 2 .
(3) 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.
(4) In the above embodiment, the ball bearings 54 and 56, which are deep groove ball bearings, are provided between the inner peripheral surfaces of the center holes 50a and 51a of the input members 50 and 51 and the outer peripheral surfaces of the eccentric portions 42a and 42b, respectively. Although the case where the input members 50 and 51 are rotatably supported with respect to the eccentric portions 42a and 42b has been described, the present invention is not limited to this, and the deep groove ball bearing is used instead of the deep groove ball bearing. A ball bearing or a roller bearing other than the bearing may be used as the first bearing. 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. Moreover, as a 1st bearing of this invention, it may replace with a rolling bearing and may use a sliding bearing.
  For example, as shown in FIGS. 12 to 15, needle roller bearings 500 (inner ring 501, outer ring 502, rolling element 503) and needle roller bearings 600 (inner ring 601, outer ring 602, rolling element 603) are used as the first bearings. , One input member 50 is rotatably supported by the eccentric portion 42a via the needle roller bearing 500, and the other input member 51 is rotatably supported by the eccentric portion 42b via the needle roller bearing 600. . In this case, FIG. 12 corresponds to FIG. 5, FIG. 13 corresponds to FIG. 9, FIG. 14 corresponds to FIG. 10, and FIG. 15 corresponds to FIG. A needle roller bearing 600 is provided between the inner peripheral surface of the center hole 50a of one input member 50 and the outer peripheral surface of the eccentric portion 42a, and the needle roller bearing 600 is replaced with the ball bearing 56 described in the above embodiment. The member 51 is disposed between the inner peripheral surface of the center hole 51a and the outer peripheral surface of the eccentric portion 42b.
(4) In the above-described embodiment, the outer peripheral surface of the output member 53 can be brought into contact with the inner peripheral surface of the pin insertion hole 50b of the input member 50 at a portion interposed between the screw portion 53a and the head portion 53b. When the needle roller bearing 55 as the second bearing and the needle roller bearing 57 as the second bearing that can contact the inner peripheral surface of the pin insertion hole 51b of the input member 51 are respectively attached. Although demonstrated, this invention is not limited to this, It may replace with a needle roller bearing and may use roller bearings and ball bearings other than a needle roller bearing. Examples of such ball bearings and roller bearings include deep groove ball bearings, angular ball bearings, cylindrical roller bearings, rod roller bearings, tapered roller bearings, and self-aligning roller bearings. Further, as the second bearing of the present invention, a sliding bearing may be used instead of the rolling bearing.
DESCRIPTION OF SYMBOLS 1 ... Motor rotational force transmission apparatus, 2 ... Housing, 20 ... 1st housing element, 20a ... Shaft penetration hole, 21 ... 2nd housing element, 21a ... Inner flange, 22 ... 3rd housing element, 22a ... Shaft Insertion hole, 22b ... cylindrical part, 23 ... convex part, 24 ... seal member, 25 ... annular member, 27 ... convex part, 28 ... seal member, 3 ... rear differential, 30 ... differential case, 30a ... accommodation space, 30b ... Shaft insertion hole, 30c ... flange, 300c ... pin mounting hole, 31 ... pinion gear shaft, 32 ... pinion gear, 33 ... side gear, 33a ... shaft coupling hole, 34, 35 ... ball bearing, 36 ... pin, 4 ... electric motor, 40 ... Stator, 41 ... Rotor, 42 ... Motor shaft, 42a, 42b ... Eccentric part, 43 ... Mounting bolt, 44 ... Ball 45, sleeve, 46 ... ball bearing, 47 ... resolver, 470 ... stator, 471 ... rotor, 5 ... deceleration transmission mechanism, 50, 51 ... input member, 50a, 51a ... center hole, 50b, 51b ... pin insertion hole , 50c, 51c ... external teeth, 52 ... rotational force applying member, 52a ... first fitting portion, 52b ... second fitting portion, 52c ... internal teeth, 53 ... output member, 53a ... screw portion, 53b ... Head, 54 ... ball bearing, 540 ... inner ring, 541 ... outer ring, 542 ... rolling element, 55 ... needle roller bearing, 550 ... race (outer ring), 551 ... needle roller, 56 ... ball bearing, 560 ... inner ring, 561 ... Outer ring, 562 ... Rolling element, 57 ... Needle roller bearing, 570 ... Race (outer ring), 571 ... Needle roller, 58 ... Spacer, 101 ... Four-wheel drive vehicle, 102 ... Engine, 103 ... Transaxle, 104 ... front wheel, 105 Rear wheel, 106 ... rear axle shaft, 107 ... front axle shaft, 100, 200, 300 ... deceleration transmission mechanism, 500 ... needle roller bearing, 501 ... inner ring, 502 ... outer ring, 503 ... rolling element, 600 ... needle roller bearing , 601 ... inner ring, 602 ... outer ring, 603 ... rolling element, O 1 ... rotation axis, L, O 2 , O ' 2 , O 3 , O' 3 , O 4 , O 5 ... axis, O 6 ... rotation axis, δ, δ 1 , δ 2 ... eccentricity, t, t ', w, w' ... operating clearance, S 1 ... fitting clearance, S 2 ... internal clearance, S, S ', D, D', d, d ' , R 1 , R 2 , R 3 , R 4 ... dimensions, P 1 , P 2 ... centrifugal force
A first fitting portion 52 a fitted to the outer peripheral surface of the convex portion 23 and a second fitting portion 52 b fitted to the outer peripheral surface of the convex portion 27 rotate on the inner peripheral surface of the rotation force applying member 52. They are provided at a predetermined interval in the direction of the axis O 1 . Further, the external teeth 50c of one input member 50 and the other input member are interposed on the inner peripheral surface of the rotation force applying member 52 between the first fitting portion 52a and the second fitting portion 52b. An involute tooth-shaped inner tooth 52 c that meshes with the outer tooth 51 c of 51 is provided. Number of teeth Z 3 of the internal teeth 52c is set to, for example, Z 3 = 208. Accordingly, the reduction ratio α of the deceleration transmission mechanism 5 is calculated from α = Z 2 / (Z 3 −Z 2 ) .

Claims (8)

  1. A rotating shaft having an eccentric portion that rotates around a first axis and has a second axis that is eccentric from the first axis as a central axis;
    A central hole disposed around the rotation axis and having a third axis as a central axis; and a plurality of through holes arranged in parallel at equal intervals around the third axis; and an inner periphery of the central hole An input member composed of an external gear having a first bearing interposed between the surface and the outer peripheral surface of the eccentric portion;
    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;
    The rotation force applied to the input member by the rotation force applying member is output as a rotational force to an output target, and a plurality of through holes having a second bearing on the outer periphery and inserted through the plurality of through holes, respectively. An output member,
    The plurality of output members are fit clearances formed between the outer peripheral surface thereof and the second bearing, and the fit clearances formed between the second bearing and the inner peripheral surfaces of the plurality of through holes. And a total dimension S ′ of radial internal clearances of the second bearing is a fitting clearance formed between the first bearing and the outer peripheral surface of the eccentric portion, and the first bearing and the center hole A reduction mechanism disposed at a position smaller than a total dimension S of a fitting clearance formed between the inner peripheral surface and a radial internal clearance of the first bearing.
  2. The first bearing has an inner ring disposed on the outer periphery of the eccentric part, an outer ring disposed on the outer periphery of the inner ring, and a rolling element disposed between the outer ring and the inner ring. And
    The dimension obtained by subtracting the outer diameter of the eccentric portion from the inner diameter of the inner ring is set as D, the dimension obtained by subtracting the outer diameter of the outer ring from the inner diameter of the center hole is set as d, and the radial internal clearance in the first bearing 2. The speed reduction mechanism according to claim 1, wherein the dimension S is set to any one of S = D + d + t, S = d + t, S = D + t, and S = t, where t is an operation clearance.
  3. The first bearing includes an inner ring raceway surface formed on an outer peripheral surface of the eccentric portion, an outer ring disposed on an outer periphery of the inner ring raceway surface, and interposed between the outer ring and the inner ring raceway surface. Rolling elements arranged as
    When the dimension obtained by subtracting the outer diameter of the outer ring from the inner diameter of the center hole is d, and the operating clearance of the radial internal clearance in the first bearing is t, the dimension S becomes S = d + t or S = t. The speed reduction mechanism according to claim 1, wherein the speed reduction mechanism is set.
  4. The first bearing includes an outer ring raceway surface formed on an inner peripheral surface of the center hole, and an inner ring disposed on an inner periphery of the outer ring raceway surface, and between the inner ring and the outer ring raceway surface. Having rolling elements arranged therebetween,
    When the dimension obtained by subtracting the outer diameter of the eccentric portion from the inner diameter of the inner ring is D and the operating clearance of the radial internal clearance in the first bearing is t, the dimension S is S = D + t or S = t. The speed reduction mechanism according to claim 1, wherein the speed reduction mechanism is set.
  5. The first bearing includes an inner ring raceway surface formed on an outer peripheral surface of the eccentric portion and an outer ring raceway surface formed on an inner peripheral surface of the center hole, and the outer ring raceway surface, the inner ring raceway surface, Rolling elements disposed between
    2. The speed reduction mechanism according to claim 1, wherein the dimension S is set to S = t, where t is an operating clearance of a radial internal clearance in the first bearing.
  6. The second bearing includes an inner ring raceway surface formed on an outer peripheral surface of the output member, and an outer ring disposed on an outer periphery of the inner ring raceway surface, and interposed between the outer ring and the inner ring raceway surface. Rolling elements arranged as
    When the fitting clearance formed between the outer peripheral surface of the outer ring and the inner peripheral surfaces of the plurality of through holes is S 1 and the internal clearance is S 2 , the dimension S ′ is S ′ = S 1. The speed reduction mechanism according to claim 1, wherein + S 2 or S ′ = S 2 is set.
  7. The second bearing has an inner ring disposed on the outer periphery of the output member, an outer ring disposed on the outer periphery of the inner ring, and a rolling element disposed between the outer ring and the inner ring. And
    The fit Aisukima formed between the outer peripheral surface and the inner ring of the inner peripheral surface of the output member together with the S 0, is formed between the inner peripheral surface of the outer peripheral surface and the plurality of through-holes of the outer ring When the fitting clearance is S 1 and the internal clearance is S 2 , the dimension S ′ is S ′ = S 0 + S 1 + S 2 , S ′ = S 0 + S 2 , S ′ = S 1 + S 2 or S The speed reduction mechanism according to claim 1, wherein ′ = S 2 is set.
  8. 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 said reduction mechanism is a reduction mechanism of any one of Claim 1 thru | or 7. A motor rotational force transmission apparatus.
JP2011265591A 2011-12-05 2011-12-05 Speed reduction mechanism, and motor torque transmission device including the same Pending JP2013117284A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2011265591A JP2013117284A (en) 2011-12-05 2011-12-05 Speed reduction mechanism, and motor torque transmission device including the same

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2011265591A JP2013117284A (en) 2011-12-05 2011-12-05 Speed reduction mechanism, and motor torque transmission device including the same
EP20120194963 EP2602509B1 (en) 2011-12-05 2012-11-30 Speed reduction mechanism, and motor torque transmission device including the same
US13/692,130 US8721484B2 (en) 2011-12-05 2012-12-03 Speed reduction mechanism, and motor torque transmission device including the same
CN 201210513187 CN103133607A (en) 2011-12-05 2012-12-04 Speed reduction mechanism, and motor torque transmission device including the same

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Country Link
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015046086A1 (en) * 2013-09-30 2015-04-02 Ntn株式会社 In-wheel motor drive device
JP2015175496A (en) * 2014-03-18 2015-10-05 セイコーエプソン株式会社 Bearing, speed reducer, robot hand, and robot

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015046086A1 (en) * 2013-09-30 2015-04-02 Ntn株式会社 In-wheel motor drive device
JP2015175496A (en) * 2014-03-18 2015-10-05 セイコーエプソン株式会社 Bearing, speed reducer, robot hand, and robot

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