JP2010007731A - Cycloid reduction gear - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a cycloid reduction gear preventing the outer ring of a rolling bearing supporting an outer pin rotatably from slipping out of a casing. <P>SOLUTION: The casing 22 of the cycloid reduction gear B includes an outer ring locking member 51 shaped in a ring attached inside the casing 22 coaxially with the axis line O of an input shaft 25, which prevents the outer ring 27g of the rolling bearing 27a from slipping out of the casing 22. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to an outer pin mounting structure provided in a casing of a cycloid reduction gear.

A conventional in-wheel motor drive device is described in, for example, Japanese Patent Application Laid-Open No. 2008-44537 (Patent Document 1). An in-wheel motor drive device described in Patent Document 1 includes a drive motor, a speed reducer that receives a driving force from the drive motor, decelerates the rotation speed, and outputs it to the wheel side, and an output shaft of the speed reducer The hub members of the wheels to be coupled are arranged coaxially. This reduction gear is a cycloid reduction mechanism, and a high reduction ratio can be obtained as compared with a conventional planetary gear reduction mechanism as a conventional reduction gear. Therefore, the required torque of the drive motor can be reduced, which is advantageous in that the size and weight of the in-wheel motor drive device can be reduced. In the cycloid reduction mechanism, the outer pin is rotatably supported on the casing by a needle roller bearing. Therefore, the contact resistance between the curved plate and the outer pin can be greatly reduced, and the torque loss of the speed reducer can be prevented.
JP 2008-44537 A

  However, Patent Document 1 does not disclose any technique for attaching an outer ring of a needle roller bearing that supports an outer pin to a casing. For this reason, if no countermeasure is taken, the outer ring may come out of the casing.

  An object of the present invention is to provide a cycloid reducer in which an outer ring of a rolling bearing that rotatably supports an outer pin does not come out of a casing.

  For this purpose, a cycloid reducer according to the present invention includes a casing, an input shaft having one end disposed inside the casing, a disc-shaped eccentric member that is eccentric from the axis of the input shaft and is coupled to one end of the input shaft, A curved plate having a plurality of curved concave portions that are circumferentially recessed at a circumferential direction, the circumference of which is attached to the outer periphery of the eccentric member so as to be rotatable relative to the outer periphery of the eccentric member, and the casing is centered on the axis of the input shaft. A plurality of outer circumferential pins are provided at equal intervals in the circumferential direction, and include an outer pin that engages with the curved concave portion as the eccentric member rotates and revolves and rotates the curved plate, and an output shaft that extracts the rotation of the curved plate. The outer pin extends parallel to the axis of the input shaft and is axially supported by the casing via a rolling bearing, and the casing is mounted coaxially with the axis of the input shaft inside the casing. It includes a ring-shaped outer ring locking member that restricts axial movement of the outer ring of the rolling bearing.

  According to the present invention, even when the outer pin is rotatably supported by the rolling bearing, the outer ring of the rolling bearing can be prevented from coming out of the casing. In addition, since the ring shape is attached coaxially with the axis of the input shaft, a plurality of outer rings arranged at equal intervals in the circumferential direction can be fixed in the axial direction by one outer ring locking member.

  The present invention is not limited to one embodiment, and the outer ring locking member includes a cylindrical portion and a flange portion formed at an axial end of the cylindrical portion, and the cylindrical portion is inserted into the casing. And the flange portion presses the end of the outer ring in the axial direction. Thereby, it is possible to prevent the outer ring of the rolling bearing from coming out of the casing.

  Preferably, the flange portion has a notch through which the outer pin passes at a circumferential position of the outer pin. As a result, the contact area between the flange portion and the outer ring of the rolling bearing can be increased, and the outer ring of the rolling bearing can be reliably prevented from coming out of the casing.

  Preferably, the casing includes an outer pin holding portion that is fitted and fixed to the casing and holds the outer pin parallel to the axis of the input shaft. The outer pin holding portion is arranged coaxially with the axis of the input shaft and accommodates the eccentric member, the curved plate, and the outer pin, and protrudes radially inward from both axial end portions of the cylindrical portion. A pair of facing ring portions and a pair of outer pin holding holes for holding a rolling bearing extending in parallel with the axis of the input shaft at the same circumferential position of the pair of ring portions, It is attached to the ring part so as not to move in the axial direction. As a result, a plurality of outer pins and rolling bearings can be modularized, and the cycloid reducer can be easily assembled and disassembled.

  Preferably, the cylindrical portion of the outer pin holding portion includes a slit that penetrates in the radial direction and allows the outer ring locking member to be inserted into the cylindrical portion from the radial direction. As a result, when the cycloid reduction gear is assembled and disassembled, the outer ring locking member can be inserted and removed through the slit, and the work efficiency of assembling and disassembling is improved.

  Thus, the cycloid reduction gear of the present invention has a ring shape that is attached to the inside of the casing coaxially with the axis of the input shaft, and includes an outer ring locking member that restricts the axial movement of the outer ring of the rolling bearing. Therefore, it is possible to suitably realize a configuration in which the outer ring of the rolling bearing is prevented from coming out of the casing, and the outer pin is rotatably supported by the rolling bearing. In addition, since it has a ring shape that is mounted coaxially with the axis of the input shaft, a plurality of outer rings arranged at equal intervals in the circumferential direction can be fixed in the axial direction with a common outer ring locking member. And the work efficiency of disassembly is improved.

  Hereinafter, embodiments of the present invention will be described in detail based on examples shown in the drawings. FIG. 1 is a longitudinal sectional view showing an in-wheel motor drive device provided with a cycloid reduction gear of this embodiment. 2 is a cross-sectional view taken along the line II-II in FIG. FIG. 3 is an enlarged view showing a portion III in FIG.

  An in-wheel motor drive device 21 as an example of a vehicle speed reduction unit is not shown in the figure, a motor part A that generates a driving force, a speed reduction part B that decelerates and outputs the rotation of the motor part A, and an output from the speed reduction part B And a wheel hub bearing portion C for transmitting to the drive wheels. The motor part A and the speed reduction part B are accommodated in the casing 22 and are mounted, for example, in a wheel housing of an electric vehicle. Or it is attached to the bogie of a railway vehicle.

  The motor part A includes a stator 23 fixed to the casing 22, a rotor 24 disposed at a position facing the inside of the stator 23 via a gap opened in the radial direction, and a rotor 24 fixedly connected to the inside of the rotor 24. 24 is a radial gap motor including a motor-side rotating member 25 that rotates integrally with the motor 24.

  The motor-side rotating member 25 is disposed from the motor part A to the speed reduction part B in order to transmit the driving force of the motor part A to the speed reduction part B, and corresponds to the input shaft of the speed reduction part B. And the one end arrange | positioned inside the deceleration part B couple | bonds with the eccentric members 25a and 25b. The motor-side rotating member 25 is fitted to the rotor 24 and supported by rolling bearings 36a and 36b at both ends of the speed reduction unit B. Further, the two disc-shaped eccentric members 25a and 25b are provided with a 180 ° phase shift so as to cancel out vibrations generated by the centrifugal force due to the eccentric motion.

  The deceleration portion B includes curved plates 26a and 26b as revolving members that are rotatably held by the eccentric members 25a and 25b, and a plurality of outer pins as outer peripheral engaging members that engage with the outer peripheral portions of the curved plates 26a and 26b. 27, a motion conversion mechanism for transmitting the rotational motion of the curved plates 26a, 26b to the wheel-side rotating member 28, and a curved plate attached to a gap between the curved plates 26a, 26b and in contact with the end surfaces of the curved plates 26a, 26b. And a center collar 29 for preventing the inclination of the lens.

  The wheel side rotation member 28 includes a flange portion 28a and a shaft portion 28b. Holes for fixing the inner pins 31 at equal intervals on the circumference centering on the rotation axis O of the wheel side rotation member 28 are formed in the end face of the flange portion 28a. A wheel hub 32 is fixed to the outer diameter surface of the shaft portion 28b.

  Referring to FIG. 2, the curved plate 26 b has a plurality of corrugations composed of trochoidal curves such as epitrochoids on the outer periphery, and a plurality of through holes 30 a and 30 b penetrating from one end face to the other end face. Have A plurality of through holes 30a are provided at equal intervals on the circumference centered on the rotation axis X of the curved plate 26b, and receive an inner pin 31 described later. The through hole 30b is provided at the center X of the curved plate 26b, and is the inner periphery of the curved plate 26b. The curved plate 26b is attached to the outer periphery of the eccentric member 25b so as to be relatively rotatable.

  The curved plate 26b is rotatably supported by the rolling bearing 41 with respect to the eccentric member 25b. The rolling bearing 41 has an inner diameter surface fitted into an outer diameter surface of the eccentric member 25b, an inner ring member 42 having an outer raceway surface 42a on the outer diameter surface, and hole walls of the outer raceway surface 42a and the through hole 30b. It is a cylindrical roller bearing provided with a plurality of rollers 44 disposed therebetween and a cage (not shown) that holds the interval between the rollers 44 adjacent in the circumferential direction. Alternatively, it may be a deep groove ball bearing. The same applies to the curved plate 26a.

  The outer pins 27 are provided at equal intervals on a circumferential track centering on the rotation axis O of the motor-side rotating member 25. Then, when the curved plates 26a, 26b revolve, the outer curved shape and the outer pin 27 engage with each other, causing the curved plates 26a, 26b to rotate.

  The outer pin 27 disposed in the casing 22 is not directly held by the casing 22, but is held by an outer pin holding portion 45 fitted and fixed to the inner wall of the casing 22, as shown in FIG. Has been. More specifically, both end portions in the axial direction are rotatably supported by needle roller bearings 27 a provided on the outer pin holding portion 45. Thus, by making the outer pin 27 rotatable to the outer pin holding portion 45, the contact resistance due to the engagement with the curved plates 26a and 26b can be reduced.

  As shown in FIG. 3, the casing 22 includes an outer pin holding portion 45 fitted and fixed to the casing 22, and an outer ring locking member 51 attached to the inner wall of the outer pin holding portion 45.

  FIG. 4 is a front view showing the outer pin holding portion 45 in a partially sectional view as seen from the direction of the axis O. FIG. FIG. 5 is a longitudinal sectional view showing a state cut along VV in FIG. 4 and viewed from the direction of the arrow. With reference to FIGS. 4 and 5, the outer pin holding portion 45 includes a cylindrical portion 46 and a pair of ring portions 47 and 48 extending radially inward from both axial end portions of the cylindrical portion 46. The outer pin holding portion 45 is fitted and fixed to the inner wall of the casing 22.

Further, at least one place on the circumference of the cylindrical portion 46 is formed with a slit 46b penetrating in the radial direction in order to insert the curved plates 26a and 26b and an outer ring locking member 51 described later. Accordingly, the curved plates 26 a and 26 b and the outer ring locking member 51 can be assembled from the radial direction of the outer pin holding part 45, and the outer ring locking member 51 can be fixed to the inner wall of the outer pin holding part 45. Needless to say, the width L _{1 of the} slit 46 b is larger than the axial width L ₂ of the outer ring locking member 51.

The ring portions 47 and 48 are provided with a plurality of outer pin holding holes 47a and 48a penetrating in the thickness direction, respectively. The outer pin holding holes 47a and 48a each extend in a direction parallel to the rotation axis O of the motor side rotation member 25, and hold the outer ring 27g of the needle roller bearing 27a. Corresponding outer pin holding holes 47a and 48a are provided at the same position in the circumferential direction and face each other. That is, the central axes O ₂ of the pair of outer pin holding holes 47a and 48a coincide. Further, when the outer pin holding portion 45 is attached to the casing 22, the central axis O ₂ becomes parallel to the rotation axis O of the motor side rotation member 25.

Thereby, the outer pin 27 can be held in parallel with the rotation axis O of the motor-side rotation member 25. The outer pin holding hole 47a, 48a may can be formed simultaneously with simultaneous machining, to match a central axis O ₂ is relatively simple.

  Further, from the viewpoint of reducing the weight of the in-wheel motor drive device 21, the casing 22 is formed of a light metal such as an aluminum alloy or a magnesium alloy. On the other hand, it is desirable to form the outer pin holding part 45, which requires high strength, from carbon steel.

  As shown in FIG. 5, the inner peripheries of the ring portions 47 and 48 are formed such that the inner diameters at both ends in the direction of the axis O are larger than the inner inner diameter. Each is provided with a step 49.

  FIG. 6 is a front view showing a state in which the outer ring locking member 51 is viewed from the direction of the axis O, and the outer pin holding portion 45 fitted to the outer ring locking member 51 is indicated by a broken line for easy understanding. . FIG. 7 is a longitudinal sectional view showing a state cut by VII-VII in FIG. 6 and viewed from the direction of the arrow. FIG. 8 is an enlarged view of the cross section shown in FIG.

  As shown in FIG. 6, the outer ring locking member 51 has a ring shape that is attached coaxially to the axis O of the motor-side rotation member 25 that serves as the input shaft of the speed reduction unit B. The outer ring locking member 51 includes a cylindrical portion 51t and a flange portion 51f formed at the end of the cylindrical portion 51t in the axis O direction. The flange portion 51f protrudes outward in the radial direction from the cylindrical portion 51t. The cylindrical portion 51t is provided with a plurality of claw portions 51n at predetermined intervals in the circumferential direction by punching or the like. The claw portion 51n has a toe slightly protruding radially outward and can be elastically deformed radially inward. And the cylindrical part 51t is inserted in the inner periphery of the ring parts 47 and 48, and the nail | claw part 51n is fitted to the level | step difference 49, and the outer ring | wheel latching member 51 is fixed inside the casing 22. FIG. As a result, the flange portion 51f comes into contact with the outer ring 27g of the needle roller bearing 27a and restricts the axial movement of the outer ring 27g (FIG. 3). Even when the outer diameter surface of the outer ring 27g receives a weak radial compressive force from the inner diameter surfaces of the outer pin holding holes 47a and 48a, the flange portion 51f contacts the inner wall of the outer pin holding portion 45 in this way. By pressing the end of the outer ring 27g in the axial direction, the outer ring 27g of the needle roller bearing 27a can be prevented from coming out of the outer pin holding part 45 of the casing 22.

  FIG. 9 is a front view showing a modified example of the outer ring locking member 51, and the outer pin holding part 45 fitted to the outer ring locking member 51 is indicated by a broken line for easy understanding. FIG. 10 is an enlarged vertical cross-sectional view showing a state where the outer ring locking member 51 shown in FIG. 9 is attached coaxially with the axis O inside the casing 22.

  The outer ring locking member 51 of the modified example protrudes further radially outward than the outer ring locking member 51 shown in FIG. In order to avoid interference with the outer pin 27, the flange portion 51 f has a notch 51 k through which the outer pin 27 penetrates at a circumferential position of the outer pin 27. As a result, the flange 51f in the vicinity of the notch 51k comes into contact with and presses the end of the outer ring 27g with a larger area than the outer ring locking member 51 shown in FIG. Thus, in the modification, the outer ring 27g of the needle roller bearing 27a can be reliably prevented from coming out of the outer pin holding part 45 of the casing 22 by the flange part 51f by the outer ring 27g.

  The motion conversion mechanism includes a plurality of inner pins 31 held by the wheel-side rotating member 28 and through holes 30a provided in the curved plates 26a and 26b. The inner pins 31 are provided at equal intervals on a circumferential track centered on the rotation axis O of the wheel side rotation member 28, and one end in the axial direction thereof is fixed to the wheel side rotation member 28. Further, in order to reduce the frictional resistance with the curved plates 26a, 26b, needle roller bearings 31a are provided at positions where they contact the inner wall surfaces of the through holes 30a of the curved plates 26a, 26b. On the other hand, the through hole 30a is provided at a position corresponding to each of the plurality of inner pins 31, and the inner diameter of the through hole 30a is the outer diameter of the inner pin 31 ("the maximum outer diameter including the needle roller bearing 31a"). The same shall apply hereinafter).

  The wheel hub bearing portion C includes a wheel hub 32 fixedly connected to the wheel-side rotating member 28 and a wheel hub bearing 33 that holds the wheel hub 32 rotatably with respect to the casing 22. The wheel hub bearing 33 is a double-row angular ball bearing, and the inner ring 33 c is fitted and fixed to the outer diameter surface of the wheel hub 32. The wheel hub 32 has a cylindrical hollow portion 32a and a flange portion 32b. A driving wheel (not shown) is fixedly connected to the flange portion 32b by a bolt 32c.

  The operation principle of the in-wheel motor drive device 21 having the above configuration will be described in detail.

  The motor unit A receives, for example, an electromagnetic force generated by supplying an alternating current to the coil of the stator 23, and the rotor 24 composed of a permanent magnet or a magnetic material rotates.

  As a result, when the motor-side rotating member 25 connected to the rotor 24 rotates, the curved plates 26 a and 26 b revolve around the rotation axis O of the motor-side rotating member 25. At this time, the outer pin 27 is engaged so as to be in rolling contact with the curved waveform of the curved plates 26 a and 26 b to cause the curved plates 26 a and 26 b to rotate in the direction opposite to the rotation of the motor-side rotating member 25.

  The inner pin 31 inserted through the through hole 30a is sufficiently thinner than the inner diameter of the through hole 30a, and comes into contact with the inner wall surface of the through hole 30a as the curved plates 26a and 26b rotate. As a result, the revolving motion of the curved plates 26 a and 26 b is not transmitted to the inner pin 31, but only the rotational motion of the curved plates 26 a and 26 b is transmitted to the wheel hub bearing portion C via the wheel-side rotating member 28.

  At this time, the wheel-side rotating member 28 disposed coaxially with the axis O takes out the rotation of the curved plates 26a and 26b as the output shaft of the speed reducing unit B, and the rotation of the motor side rotating member 25 is decelerated by the speed reducing unit B. Since it is transmitted to the wheel side rotation member 28, even when the low torque, high rotation type motor unit A is employed, it is possible to transmit the torque required for the drive wheels.

Note that the reduction ratio of the speed reduction portion B having the above-described configuration is calculated as (Z _A −Z _B ) / Z _B where Z _{A is} the number of outer pins 27 and Z _B is the number of waveforms of the curved plates 26a and 26b. The In the embodiment shown in FIG. 2, since Z _A = 12 and Z _B = 11, the reduction ratio is 1/11, and a very large reduction ratio can be obtained.

  In this way, by adopting the speed reduction unit B that can obtain a large speed reduction ratio without using a multi-stage configuration, the in-wheel motor drive device 21 having a compact and high speed reduction ratio can be obtained. Since the outer pin 27 is rotatable with respect to the outer pin holding portion 45 and the needle roller bearing 31a is provided at a position where the outer pin 27 comes into contact with the curved plates 26a and 26b of the inner pin 31, the frictional resistance is reduced. The transmission efficiency of the deceleration part B is improved.

  By employing the in-wheel motor drive device 21 according to this embodiment in an electric vehicle, the unsprung weight can be suppressed. As a result, an electric vehicle with excellent running stability can be obtained.

  In the present embodiment, two curved plates 26a and 26b of the speed reduction portion B are provided with 180 ° phase shifts. However, the number of the curved plates can be arbitrarily set. In the case of providing a sheet, it is preferable to change the phase by 120 °.

  Moreover, although the motion conversion mechanism in a present Example showed the example comprised by the inner pin 31 fixed to the wheel side rotation member 28, and the through-hole 30a provided in the curve boards 26a and 26b, Without limitation, any configuration capable of transmitting the rotation of the speed reduction unit B to the wheel hub 32 can be employed. For example, it may be a motion conversion mechanism composed of an inner pin fixed to a curved plate and a hole formed in the wheel side rotation member.

  The description of the operation in the present embodiment has been made by paying attention to the rotation of each member, but in reality, power including torque is transmitted from the motor unit A to the drive wheels. Therefore, the power decelerated as described above is converted into high torque.

  In the description of the operation in the present embodiment, power is supplied to the motor unit A to drive the motor unit A, and the power from the motor unit A is transmitted to the drive wheels. When decelerating or going down a hill, the power from the driving wheel side may be converted into high-rotation and low-torque rotation by the deceleration unit B and transmitted to the motor unit A, and the motor unit A may generate power. . Furthermore, the electric power generated here may be stored in a battery and used later for driving the motor unit A or for operating other electric devices provided in the vehicle.

  Further, a brake can be added to the configuration of this embodiment. For example, in the configuration of FIG. 1, the casing 22 is extended in the axial direction to form a space on the right side of the rotor 24 in the drawing, the rotating member that rotates integrally with the rotor 24, and the casing 22 is non-rotatable and axial. A parking brake that locks the rotor 24 by disposing a movable piston and a cylinder that operates the piston and fitting the piston and the rotating member when the vehicle is stopped may be used.

  Alternatively, it may be a disc brake in which a flange formed on a part of a rotating member that rotates integrally with the rotor 24 and a friction plate installed on the casing 22 side are sandwiched by a cylinder installed on the casing 22 side. Furthermore, a drum brake can be used in which a drum is formed on a part of the rotating member, a brake shoe is fixed to the casing 22 side, and the rotating member is locked by friction engagement and self-engagement.

  In the present embodiment, an example of a cylindrical roller bearing is shown as the bearing 41 that supports the curved plates 26a and 26b. However, the present invention is not limited to this, and for example, a plain bearing, a deep groove ball bearing, a tapered roller bearing, and a needle roller Bearings, spherical roller bearings, angular contact ball bearings, 4-point contact ball bearings, etc., whether they are plain bearings or rolling bearings, regardless of whether the rolling elements are rollers or balls, All bearings can be applied, whether double row or single row. Similarly, any type of bearing can be adopted for bearings arranged in other locations.

  Further, in this embodiment, an example is adopted in which a radial gap motor including a stator fixed to the casing of the motor part A and a rotor disposed at a position facing the inner side of the stator with a radial gap is provided. Although shown, it is not restricted to this, The motor of arbitrary structures is applicable. For example, an axial gap motor in which the stator and the rotor are arranged to face each other via a gap opened in the axial direction may be used.

  Furthermore, the electric vehicle on which the in-wheel motor drive device 21 is mounted may have a rear wheel as a drive wheel, a front wheel as a drive wheel, or a four-wheel drive vehicle. In the present specification, “electric vehicle” is a concept including all vehicles that obtain driving force from electric power, and should be understood as including, for example, a hybrid vehicle.

  As mentioned above, although embodiment of this invention was described with reference to drawings, this invention is not limited to the thing of embodiment shown in figure. Various modifications and variations can be made to the illustrated embodiment within the same range or equivalent range as the present invention.

  The present invention can be employed in a cycloid reducer used in an in-wheel motor drive device or the like.

It is a longitudinal cross-sectional view which shows the in-wheel motor drive device which becomes one Example of this invention. It is sectional drawing in II-II of FIG. FIG. 2 is an enlarged view around an outer pin in FIG. 1. It is a front view which shows the state which looked at the outer pin holding | maintenance part from the axial direction in a partial cross section. It is sectional drawing in VV of FIG. It is a front view which shows the state which looked at the outer ring | wheel latching member from the axial direction. It is a longitudinal cross-sectional view in VII-VII of FIG. It is the figure which expanded the cross section shown in FIG. It is a front view which shows the state which looked at the modification of the outer ring | wheel latching member from the axial direction. It is a longitudinal cross-sectional view which shows the state by which the outer ring | wheel latching member of the modification was attached to the inside of a casing.

Explanation of symbols

  21 in-wheel motor drive device, 22 casing, 23 stator, 24 rotor, 25 motor side rotating member, 25a, 25b eccentric member, 26a, 26b curved plate, 27 outer pin, 27a needle roller bearing, 27g outer ring, 28 wheel side Rotating member, 29 Center collar, 30a, 30b Through hole, 31 Inner pin, 31a Needle roller bearing, 32 Wheel hub, 33 Wheel hub bearing, 45 Outer pin holding part, 46, Cylindrical part, 46b Curved plate insertion hole, 47 , 48 Ring part, 47a, 48a Outer pin holding hole, 49 steps, 51 outer ring locking member, 51t cylindrical part, 51f flange part, 51n claw part, 51k notch.

Claims (5)

A casing,
An input shaft having one end disposed inside the casing;
A disc-shaped eccentric member eccentric from the axis of the input shaft and coupled to one end of the input shaft;
A curved plate having an inner periphery attached to the outer periphery of the eccentric member so as to be relatively rotatable, an outer periphery formed of a wavy curve, and having a plurality of curved concave portions recessed in the radial direction;
A plurality of outer pins arranged at equal intervals in the circumferential direction around the axis, and engaged with the curved recess as the eccentric member rotates and revolves and rotates the curved plate,
An output shaft for taking out the rotation of the curved plate,
The outer pin extends in parallel with the axis, and an axial end is rotatably supported by the casing via a rolling bearing,
The said casing is a cycloid reduction gear which is the ring shape attached coaxially with the said axis line inside a casing, Comprising: The outer ring | wheel latching member which controls the axial direction movement of the outer ring | wheel of the said rolling bearing is included. The outer ring locking member includes a cylindrical portion and a flange portion formed at an axial end of the cylindrical portion,
The cycloid reducer according to claim 1, wherein the cylindrical portion is inserted into and fitted into the casing, and the flange portion presses an end of the outer ring in the axial direction.   The cycloid reducer according to claim 2, wherein the flange portion has a notch through which the outer pin penetrates at a circumferential position of the outer pin. The casing includes an outer pin holding portion that is fitted and fixed to the casing and holds the outer pin parallel to the axis of the input shaft.
The outer pin holding part is
A cylindrical portion disposed coaxially with the axis to accommodate the eccentric member, the curved plate, and the outer pin;
A pair of ring portions projecting radially inward from both axial ends of the cylindrical portion and facing each other;
A pair of outer pin holding holes that extend parallel to the axis and hold the rolling bearing at the same circumferential position of the pair of ring portions;
The cycloid reduction gear according to any one of claims 1 to 3, wherein the outer ring locking member is attached to the ring portion so as not to be axially movable.   The cycloid reducer according to claim 4, wherein the cylindrical portion of the outer pin holding portion includes a slit that penetrates in a radial direction and allows the outer ring locking member to be inserted into the cylindrical portion from the radial direction.

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