JP2010071462A - In-wheel motor driving device - Google Patents

In-wheel motor driving device Download PDF

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Publication number
JP2010071462A
JP2010071462A JP2009142356A JP2009142356A JP2010071462A JP 2010071462 A JP2010071462 A JP 2010071462A JP 2009142356 A JP2009142356 A JP 2009142356A JP 2009142356 A JP2009142356 A JP 2009142356A JP 2010071462 A JP2010071462 A JP 2010071462A
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Japan
Prior art keywords
casing
peripheral
holding
wheel motor
motor drive
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Pending
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JP2009142356A
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Japanese (ja)
Inventor
Yuichi Ito
Tomoaki Makino
Minoru Suzuki
Ken Yamamoto
雄一 伊藤
山本  憲
智昭 牧野
稔 鈴木
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Ntn Corp
Ntn株式会社
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Priority to JP2008213650 priority Critical
Application filed by Ntn Corp, Ntn株式会社 filed Critical Ntn Corp
Priority to JP2009142356A priority patent/JP2010071462A/en
Publication of JP2010071462A publication Critical patent/JP2010071462A/en
Pending legal-status Critical Current

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H1/00Toothed gearings for conveying rotary motion
    • F16H1/28Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/32Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear

Abstract

To provide an in-wheel motor drive device capable of preventing vibration due to insufficient support rigidity when a peripheral engagement member holding portion is newly provided inside a casing.
A speed reduction portion B of an in-wheel motor drive device 21 includes a casing 22, an input shaft 25 disposed inside the casing 22, eccentric members 25a and 25b coupled to the input shaft 25, and an inner periphery thereof is eccentric. Revolving members 26a and 26b which are attached to the outer periphery of the members 25a and 25b so as to be relatively rotatable and perform revolving motion, outer peripheral engagement members 27 which cause the revolving motion of the revolving members 26a and 26b, and rotation of the revolving members 26a and 26b An output shaft 28 that extracts motion, an outer peripheral engagement member holding portion 45 that is attached to the inside of the casing 22 and supports the outer peripheral engagement member 27, and an inner wall of the casing 22 and an outer peripheral surface of the outer peripheral engagement member holding portion 45. And a pressing member that is inserted while being elastically deformed, and that presses the outer peripheral engagement member holding portion radially inward.
[Selection] Figure 1

Description

  The present invention relates to a support structure for an outer peripheral engagement member of an in-wheel motor drive device.
  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 number of rotations, 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 and in series. This speed reducer is a cycloid speed reduction mechanism, and a high speed reduction ratio can be obtained as compared with a planetary gear speed reduction mechanism that is general as a conventional speed reducer. 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 peripheral engagement member is rotatably supported on the casing by a needle roller bearing. Therefore, the contact resistance between the revolution member and the outer peripheral engagement member can be greatly reduced, and the torque loss of the reduction gear can be prevented.
JP 2008-44537 A
  The casing of the cycloid reduction mechanism is fastened and fixed to the casing of the drive motor on one side in the axial direction, and is fixed to the casing of the hub member on the other side in the axial direction. Moreover, the outer periphery engaging member of a cycloid reduction mechanism is pin shape, is supported in parallel with the axis line of an in-wheel motor drive device, and engages with the outer periphery of a revolution member. Moreover, for the convenience of assembly, it is necessary to divide the casing of the cycloid reduction mechanism into two in the axial direction, arrange the outer peripheral engagement member and the revolution member inside the casing, and join these two casings. Here, it is difficult to assemble the casing on one side supporting one side in the axial direction of the outer peripheral engagement member and the casing on the other side supporting the other side in the axial direction of the outer peripheral engagement member with respect to the positional relationship with high accuracy. There is a possibility that the extending direction of the outer peripheral engaging member is slightly non-parallel to the axis. If the parallelism with respect to the axis is poor, an edge load due to point contact acts between the outer peripheral engagement member and the revolution member, and there is a concern that the cycloid reduction mechanism may be worn away and the durability may be reduced.
  For this reason, it is possible to newly provide an outer peripheral engagement member holding part that is attached to the inner wall of the casing and supports both ends of the outer peripheral engagement member in common. According to this outer periphery engagement member holding part, it is possible to make the extending direction of the outer periphery engagement member parallel to the axis without depending on the assembly accuracy of the one side casing and the other side casing.
  By the way, for the convenience of assembly, it is difficult to make the inner wall of the casing and the outer wall of the outer peripheral engagement member holding portion completely adhere to each other, and in the design, a gap is provided between the casing and the outer peripheral engagement member holding portion. Can be considered.
  However, when this annular gap is provided, there are concerns about the following problems. First, it does not support the outer peripheral engagement member holding portion in the radial direction but also causes vibration of the cycloid reduction mechanism. Second, when the casing is formed of a light metal such as aluminum and the outer peripheral engagement member holding portion is formed of carbon steel with the aim of reducing the weight of the cycloid reduction mechanism, the materials of different physical properties are adjacent to each other. The difference causes a gap between the casing and the outer peripheral engagement member holding portion to open, causing the cycloid reduction mechanism to vibrate.
  The objective of this invention is providing the in-wheel motor drive device which can prevent suitably the vibration of a cycloid reduction mechanism even when it is a case where an outer periphery engaging member holding part is newly provided in a casing inside.
  For this purpose, an in-wheel motor drive device according to the present invention includes a motor unit that rotationally drives a motor-side rotating member, a speed-reducing unit that decelerates the rotation of the motor-side rotating member and transmits the rotation to the wheel-side rotating member, and the wheel It is assumed that a wheel hub fixedly connected to the side rotating member is provided. The speed reducer includes a casing that is an outer shell of the speed reducer, 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, 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 revolves around the axis as the input shaft rotates, and engages with the outer periphery of the revolution member to cause the rotation of the revolution member. An outer periphery engaging member to be rotated, an output shaft for taking out the rotation of the revolving member, a ring shape centering on the axis, and an outer periphery engaging member holding portion that is attached to the inside of the casing and supports the outer periphery engaging member; And a pressing member that is inserted between the inner wall of the casing and the outer peripheral surface of the outer peripheral engaging member holding portion while being elastically deformed and presses the outer peripheral engaging member holding portion radially inward.
  According to the present invention, the pressing member is inserted between the inner wall of the casing and the outer peripheral surface of the outer peripheral engagement member holding portion while being elastically deformed to press the outer peripheral engagement member holding portion radially inward. For this reason, it is possible to support the outer peripheral engagement member holding portion in the radial direction. Therefore, even when the outer peripheral engagement member holding portion is newly provided inside the casing, the concern about vibration can be solved.
  The present invention is not limited to one embodiment, and the pressing member may be made of rubber or a metal member formed of metal. According to this embodiment, since it is metal, durability improves.
  The present invention is not limited to one embodiment, and the metal member may be provided at one or two locations of the annular gap. However, as a preferred embodiment, the metal member is at least three or more in the circumferential direction. Is inserted. Thereby, it can support so that an outer periphery engaging member holding | maintenance part may be arrange | positioned coaxially with an axis line.
  Preferably, the metal member is a spring pin extending in parallel with the axis. Alternatively, it is a pin having a V-shaped cross section that extends parallel to the axis. These pins can be inserted between the inner wall of the casing and the outer peripheral surface of the outer peripheral engagement member holding portion while being easily elastically deformed, and the concern about vibration can be eliminated with a simple configuration. it can.
  Preferably, the inner wall of the casing includes a recess that engages with the metal member. Instead of the inner wall of the casing or together with the inner wall of the casing, the outer peripheral surface of the outer peripheral engaging member holding portion includes a concave portion that engages with the metal member. Thereby, a metal member can be arrange | positioned easily. Moreover, the relative rotation of the outer periphery engaging member holding | maintenance part with respect to a casing can be suppressed.
  The present invention is not limited to an embodiment, and the outer peripheral surface of the outer peripheral engagement member holding portion faces the inner wall of the casing through a gap, and the pressing member is a polymer material member formed of a polymer material. It may be. According to this embodiment, by using a pressing member formed of a polymer material having a large vibration suppressing effect, for example, a low repulsion material, vibration generated from the speed reduction unit can be absorbed by the polymer material member. it can.
  In addition, since the polymer material member is inserted while being elastically deformed, the outer peripheral engagement member holding portion exhibits a supporting force so as to coincide with the rotation axis of the speed reduction portion. Therefore, generation | occurrence | production of the vibration of a deceleration part can be suppressed.
  Although the present invention is not limited to one embodiment, grooves that extend in the axial direction and receive a member made of a polymer material may be formed on the inner wall of the casing and the outer peripheral surface of the outer peripheral engagement member holding portion. . According to this embodiment, it is possible to absorb vibrations in the rotational direction of the speed reducing portion.
  The cross-sectional shape of the groove is not particularly limited, but as a preferred embodiment, the groove has a V-shaped cross section perpendicular to the axis. According to such an embodiment, it becomes possible to relieve the circumferential shear load acting on the polymer material member between the inner wall of the casing and the outer peripheral surface of the outer peripheral engagement member holding portion, and the polymer material The durability of the member is improved.
  Alternatively, as another embodiment, the groove has an arch shape in a cross section perpendicular to the axis. Here, the arch shape may be a parabolic curve or a catenary. Moreover, a Gothic arch shape may be sufficient.
  As a preferred embodiment, the groove has a chamfered portion at the boundary between the inner wall and the groove of the casing and the boundary between the outer peripheral surface of the outer peripheral engagement member holding portion and the groove. According to such an embodiment, the boundary between the inner wall of the casing and the groove and the boundary between the outer peripheral surface of the outer peripheral engagement member holding portion and the groove are not angular, so the circumferential direction from these boundaries to the polymeric material member It is possible to avoid the action of the shear load.
  In a preferred embodiment, the polymer material member extends along the groove and has a circular cross-sectional shape. According to this embodiment, the polymer material member does not contact the boundary between the inner wall and the groove of the casing and the boundary between the outer peripheral surface of the outer peripheral engagement member holding portion and the groove, and the inner wall of the casing and the outer peripheral engagement member It becomes possible to disperse the circumferential shear load acting on the polymer material member between the outer peripheral surface of the holding portion.
  As a preferred embodiment, the speed reducing portion further includes a metal member interposed between the inner wall of the casing and the outer peripheral surface of the outer peripheral engagement member holding portion. According to such an embodiment, the reliability is improved.
  As a preferred embodiment, the gap between the inner wall of the casing and the outer peripheral surface of the outer peripheral engagement member holding portion is larger than the component perpendicular to the axis of vibration of the outer peripheral engagement member holding portion. According to this embodiment, the polymer material member can efficiently absorb the vibration of the speed reducing portion. Further, the outer peripheral engaging member holding portion vibrates and does not contact the inner wall of the casing, so that abnormal noise can be prevented.
  Thus, the present invention provides a pressing member that is inserted while being elastically deformed between the inner wall of the casing and the outer peripheral surface of the outer peripheral engagement member holding portion and presses the outer peripheral engagement member holding portion radially inward. Prepare. Therefore, it is possible to favorably support the outer peripheral engagement member holding portion in the radial direction, and even when the outer peripheral engagement member holding portion is newly provided inside the casing, the concern about vibration can be eliminated. .
It is a longitudinal cross-sectional view which shows the in-wheel motor drive device which becomes one Example of this invention. It is a cross-sectional view of the deceleration part in the Example. It is a figure which expands and shows a part of FIG. It is a figure which expands and shows the modification which becomes a part of FIG. It is a figure which expands and shows the modification which becomes a part of FIG. It is a figure which expands and shows the modification which becomes a part of FIG. It is a figure which expands and shows the modification which becomes a part of FIG. It is a figure which expands and shows the modification which becomes a part of FIG. It is a figure which expands and shows the modification which becomes a part of FIG. It is a figure which expands and shows the modification of this invention. It is another Example of this invention, Comprising: It is a cross-sectional view of a deceleration part. It is a figure which expands and shows the comparative example used as a part of FIG. It is a figure which expands and shows a part of FIG. It is a figure which expands and shows the modification which becomes a part of FIG.
  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 of the present embodiment. FIG. 2 is a cross-sectional view of the in-wheel motor drive device of the present embodiment.
  An in-wheel motor drive device 21 that is mounted under the floor of a vehicle and drives a wheel includes a motor unit A that generates a driving force, a deceleration unit B that decelerates and outputs the rotation of the motor unit A, and a reduction unit B And a wheel hub bearing portion C for transmitting the output to drive wheels (not shown). Then, the motor part A, the speed reduction part B, and the wheel hub bearing part C are arranged in series in the direction of the axis O. The motor part A and the speed reduction part B are accommodated in the casing 22, and the wheel hub bearing part C is rotatably supported by the casing 22. The outer wall of the casing 22 is attached to, for example, a wheel housing of an electric vehicle via a knuckle, a suspension, or the like. 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 disk-shaped rotor 24 disposed opposite to the inner side of the stator 23 via an axially opened gap, and a rotor 24 fixedly connected to the inner side of the rotor 24. 24 is an axial gap motor including a motor-side rotation 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 other end of the motor-side rotating member 25 is fitted to the rotor 24 and is 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 change in the circumferential direction in order to cancel each other the 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 that transmits the rotational motion of the curved plates 26a and 26b to the wheel-side rotating member 28, and a speed reduction portion casing 22b that accommodates these members therein. The speed reduction part casing 22b, which is a part of the casing 22, is cylindrical and is fitted to the casing 22 of the motor part A on one side in the direction of the axis O, and the casing 22c of the wheel hub bearing part C on the other side. Combine with.
  The wheel-side rotation member 28 is disposed from the speed reduction part B to the wheel hub bearing part C, and has a flange part 28a and a shaft part 28b. The flange portion 28a is in the speed reduction portion B, and holes 28h for fixing the inner pins 31 are formed on the end surface of the flange portion 28a at equal intervals on the circumference around the rotation axis O of the wheel side rotation member 28. ing. The shaft portion 28b extends from the flange portion 28a to the wheel hub bearing portion C, and the wheel hub 32 is fixed to the outer diameter surface of the shaft portion 28b.
  Referring to FIG. 2, the curved plate 26 a has a plurality of corrugations composed of trochoidal curves such as epitrochoids on the outer peripheral portion, 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 26a, and receive an inner pin 31 described later. The through hole 30b is provided at the center X of the curved plate 26a, and is the inner periphery of the curved plate 26a. The curved plate 26a is attached to the outer periphery of the eccentric member 25a so as to be relatively rotatable.
  The curved plate 26a is supported by the rolling bearing 41 so as to be rotatable with respect to the eccentric member 25a. The rolling bearing 41 includes an inner ring member 42, an outer ring member 43, a plurality of rollers 44 disposed between the outer raceway surface of the inner ring member 42 and the inner raceway surface of the outer ring member 43, and rollers 44 adjacent in the circumferential direction. It is a cylindrical roller bearing provided with the holder | retainer (illustration omitted) which hold | maintains these space | intervals. Alternatively, the rolling bearing 41 may be a deep groove ball bearing.
  The inner periphery of the inner ring member 42 is fitted to the outer peripheral surface of the eccentric member 25 a, and the outer periphery of the inner ring member 42 becomes the inner raceway surface of the roller 44. The inner periphery of the outer ring member 43 is the outer raceway surface of the roller 44, and the outer periphery of the outer ring member 43 is fitted to the inner periphery of the through hole 30b of the curved plate 26a. The same applies to the curved plate 26b.
  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. The rotation axis X is eccentric from the rotation axis O. 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 or the speed reduction part casing 22b of the speed reduction part B, but is an outer pin fitted and fixed to the inner wall of the speed reduction part casing 22b. It is held by the holding unit 45. 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 attaching the outer pin 27 to the outer pin holding portion 45 so as to be rotatable, the contact resistance due to the engagement with the curved plates 26a, 26b can be reduced.
  The outer pin holding portion 45 as the outer periphery engaging member holding portion has a ring shape centering on the axis O, and includes a cylindrical portion 46 and a pair of ring portions 47 extending radially inward from both axial ends of the cylindrical portion. , 48. The outer pin holding portion 45 is attached to the inner wall of the casing 22. A detent pin 49 that prevents the rotation of the outer pin holding portion 45 is attached between the outer peripheral surface of the cylindrical portion 46 and the speed reduction portion casing 22b.
  The ring portions 47 and 48 are provided with a plurality of outer pin holding holes 47h and 48h penetrating in the thickness direction, respectively. The outer pin holding holes 47h and 48h each extend in a direction parallel to the rotation axis O of the motor side rotating member 25 and hold the outer ring 27g of the needle roller bearing 27a. The outer pin holding hole 47h of the ring portion 47 and the outer pin holding hole 48h of the ring portion 48 are provided at the same position in the circumferential direction and face each other. When the outer pin holding part 45 is attached to the casing 22, the central axes of the outer pin holding holes 47 h and 48 h facing each other are parallel to the rotation axis O of the motor side rotation member 25.
  Thereby, the outer pin holding part 45 can hold the outer pin 27 in parallel with the rotation axis O of the motor side rotating member 25. Since the outer pin holding holes 47h and 48h can be formed coaxially by simultaneous processing, it is relatively easy to match the center of the outer pin holding hole 47h with the center of the outer pin holding hole 48h.
  From the viewpoint of reducing the weight of the in-wheel motor drive device 21, the casing 22 including the casings 22b and 22c 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.
  FIG. 3 is an enlarged view of a region indicated by D in FIG. A plurality of spring pins 51 are inserted at equal intervals in the circumferential direction between the inner wall of the speed reduction unit casing 22 b and the outer peripheral surface of the outer pin holding unit 45. The spring pin 51 is a metal tubular member (metal member) extending in parallel with the axis O, and a slit 51s is formed in a part thereof and has a C-shaped cross section. An engagement groove 52 that engages with the spring pin 51 is formed on the inner wall of the speed reduction unit casing 22b. The engagement groove 52 extending in parallel with the axis O has a semicircular cross section and is substantially the same as the outer diameter of the spring pin 51. An engaging groove 53 that engages with the spring pin 51 is formed on the outer peripheral surface of the outer pin holding portion 45. The engagement groove 53 extending in parallel with the axis O has a semicircular cross section and is substantially the same as the outer diameter of the spring pin 51. The spring pin 51 is inserted into the engagement grooves 52 and 53 while being elastically deformed, and has a diameter smaller than that of the original shape so that the width of the slit 51s is narrowed. Therefore, the spring pin 51 presses the engagement grooves 52 and 53 in the radial direction so as to return to the original shape. Since the spring pin 51 is made of a metal that exhibits elasticity, such as spring steel used for the spring, it has a larger Young's modulus than rubber.
  When the in-wheel motor drive device 21 is assembled, the spring pin 51 is moved from the joint surface between the motor part A and the speed reduction part B to the space between the inner wall of the speed reduction part casing 22b and the outer peripheral surface of the outer pin holding part 45. It may be inserted in parallel with O.
  At least three spring pins 51 are arranged in the circumferential direction and press the outer pin holding portion 45 in the radial direction toward the axis O. For this reason, a force that supports the outer pin holding portion 45 in the center inside the speed reduction portion casing 22b, that is, the position of the axis O acts in the radial direction to increase the support rigidity of the outer pin holding portion 45 and hold the outer pin. The vibration of the part 45 can be prevented. In this embodiment, as shown in FIG. 2, spring pins 51 are provided at six locations at equal intervals in the circumferential direction.
  Further, the speed reduction part B of the present embodiment becomes hot, and a gap between the inner wall of the speed reduction part casing 22b and the outer peripheral surface of the outer pin holding part 45 due to the difference in the linear expansion coefficient between the speed reduction part casing 22b and the outer pin holding part 45. Since the spring pin 51 continues to press the outer pin holding portion 45 even when the increase in the number of pins is increased, the support rigidity of the outer pin holding portion 45 can be increased to prevent vibration of the outer pin holding portion 45. it can. Therefore, according to the present embodiment, even when the casing 22 is made of light metal for weight reduction, it is advantageous for preventing vibration.
  Next, each modification of the present invention will be described sequentially. 4 to 10 are longitudinal sectional views showing modified examples of the present invention, in which the area D in FIG. 2 is enlarged.
  In the modification shown in FIG. 4, the engagement groove 53 has a rectangular cross section. Other basic configurations are the same as those of the embodiment described with reference to FIGS. Even in the modification of FIG. 4, the spring pin 51 can press the engagement grooves 52 and 53, and the support rigidity of the outer pin holding portion 45 can be increased.
  In the modification shown in FIG. 5, the engagement groove 52 and the engagement groove 53 are rectangular in cross section. Other basic configurations are the same as those of the embodiment described with reference to FIGS. Even in the modification of FIG. 5, the spring pin 51 can press the engaging grooves 52 and 53, and the support rigidity of the outer pin holding portion 45 can be increased.
  In the modification shown in FIG. 6, the spring pin 51 has a V-shaped cross section, the engagement groove 52 and the engagement groove 53 have a rectangular cross section, and the other basic configuration is the same as the embodiment described with reference to FIGS. It is. The angle of the central portion 51c in the cross section of the spring pin 51 is an acute angle of 60 degrees, but may be a right angle or an obtuse angle. The both side edges 51k are made to coincide with each other in the circumferential direction, and the center to the center part 51c of both side edges 51k are made to coincide with each other in the radial direction to improve stability. Specifically, both side edges 51k in the cross section of the spring pin 51 are brought into contact with the outer peripheral surface of the outer pin holding portion 45, the center portion 51c is brought into contact with the inner wall of the speed reduction portion casing 22b, and the outer pin holding portion 45 and the speed reduction portion casing are contacted. A spring pin 51 having a V-shaped cross section is interposed between the spring 22b and 22b while being elastically deformed. Even in the modification of FIG. 6, the spring pin 51 can press the engagement grooves 52 and 53, and the support rigidity of the outer pin holding portion 45 can be increased.
  In the modification shown in FIG. 7, no engagement groove is provided on the outer peripheral surface of the outer pin holding portion 45. Instead, an engagement groove 52 having a depth for accommodating almost the entire spring pin 51 is provided on the inner wall of the speed reduction unit casing 22b. Other basic configurations are the same as those of the embodiment described with reference to FIGS. The engagement groove 52 is a U-shaped cross section cut outward in the radial direction, and the depth of the engagement groove 52 is slightly shallower than the outer diameter of the spring pin 51. For this reason, the spring pin 51 comes into contact with the outer peripheral surface of the outer pin holding portion 45 and is inserted between the outer pin holding portion 45 and the speed reduction portion casing 22b while being elastically deformed. Even in the modification of FIG. 7, the spring pin 51 can press the outer peripheral surface of the outer pin holding portion 45 and the engaging groove 52, and the support rigidity of the outer pin holding portion 45 can be increased.
  In the modification shown in FIG. 8, the spring pin 51 has a V-shaped cross section, and instead of providing an engagement groove on the outer peripheral surface of the outer pin holding portion 45, almost the entire spring pin 51 is accommodated in the inner wall of the speed reduction portion casing 22b. An engagement groove 52 having a depth to be formed is provided, and the engagement groove 52 has a rectangular cross section. Other basic configurations are the same as the embodiment described with reference to FIGS. 1 to 3 and the modification described with reference to FIG. 6. Even in the modification of FIG. 8, the spring pin 51 can press the outer peripheral surface of the outer pin holding portion 45 and the engaging groove 52, and the support rigidity of the outer pin holding portion 45 can be increased.
  In the modification shown in FIG. 9, no engagement groove is provided on the inner wall of the speed reduction unit casing 22b. Instead, an engagement groove 53 having a depth for accommodating substantially the entire spring pin 51 is provided on the outer peripheral surface of the outer pin holding portion 45. Other basic configurations are the same as those of the embodiment described with reference to FIGS. The engagement groove 53 is a U-shaped cross section cut inward in the radial direction, and the depth of the engagement groove 53 is slightly shallower than the outer diameter of the spring pin 51. For this reason, the spring pin 51 contacts the inner wall of the speed reduction part casing 22b, and is inserted between the outer pin holding part 45 and the speed reduction part casing 22b while being elastically deformed. Even in the modified example of FIG. 9, the spring pin 51 can press the engagement groove 53 and the inner wall of the speed reduction portion casing 22 b, thereby increasing the support rigidity of the outer pin holding portion 45.
  In the modification shown in FIG. 10, no engagement groove is provided on the inner wall of the speed reduction unit casing 22b. Instead, an engagement groove 53 having a depth for accommodating substantially the entire spring pin 51 is provided on the outer peripheral surface of the outer pin holding portion 45. The engagement groove 53 is rectangular in cross section. The spring pin 51 has a V-shaped cross section, and both side edges 51k in the cross section are brought into contact with the inner wall of the speed reduction portion casing 22b, the central portion 51c is brought into contact with the bottom surface of the engaging groove 53 of the outer pin holding portion 45, and the outer pin holding portion. A spring pin 51 having a V-shaped cross section is inserted between 45 and the speed reducer casing 22b while being elastically deformed. Other basic configurations are the same as the embodiment described with reference to FIGS. 1 to 3 and the modification described with reference to FIG. 6. Even in the modified example of FIG. 10, the spring pin 51 can press the engagement groove 53 and the inner wall of the speed reduction unit casing 22 b, thereby increasing the support rigidity of the outer pin holding unit 45.
  6, 8, and 10, the posture of the spring pin 51 having a V-shaped cross section may be reversed in the radial direction inside and outside.
  Returning to FIG. 1 and FIG. 2, the motion conversion mechanism of the speed reduction unit B includes a plurality of inner pins 31 held by the wheel side rotation member 28 and through holes 30 a provided in the curved plates 26 a and 26 b. Composed. 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. In order to reduce the frictional resistance with the curved plates 26a, 26b, a needle roller bearing 31a is provided at a position where it abuts against the inner wall surface of the through hole 30a of the curved plates 26a, 26b of the inner pin 31. 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 inner pin 31 is an inner engagement member that is closer to the inner diameter side than the outer pin 27 and engages with the through holes 30a of the curved plates 26a and 26b.
  The wheel hub bearing portion C includes a wheel hub 32 fixedly connected to the wheel-side rotating member 28, a wheel hub bearing 33 that rotatably holds the wheel hub 32, and a casing 22c that supports the wheel hub bearing 33. The wheel hub bearing portion casing 22c, which is a part of the casing 22, has a cylindrical shape and is fastened to the speed reduction portion casing 22b of the speed reduction portion B. The wheel hub bearing 33 is a double-row angular ball bearing. 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 hole 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 configured by engagement 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, it may be a radial gap motor in which the stator and the rotor are arranged so as to face each other through a gap opened in the radial direction.
  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.
  Next, another embodiment of the present invention will be described. FIG. 11 is a cross-sectional view showing another embodiment of the present invention. FIG. 12 is an enlarged view of the region indicated by E in FIG. 11 and represents a comparative example compared with the present invention. FIG. 13 is an enlarged view of the area indicated by E in FIG. In the other embodiments to be described below, the same reference numerals are given to the configurations common to the above-described embodiments, the description thereof is omitted, and different configurations will be described below. In another embodiment, a plurality of polymeric material members 61 are inserted at equal intervals in the circumferential direction between the inner wall of the speed reduction unit casing 22 b and the outer peripheral surface of the outer pin holding unit 45. The polymer material member 61 is a cylindrical member extending in parallel with the axis O, and is formed of a polymer material.
  The polymer material is preferably a material that absorbs vibration, such as rubber, synthetic resin, silicon resin, synthetic fiber, and the like. The polymer material member 61 is sandwiched between the inner wall of the speed reduction portion casing 22b and the outer peripheral surface of the outer pin holding portion 45 and elastically deforms to the compression side, and presses the outer peripheral surface of the outer pin holding portion 45 in the inner diameter direction. . As a material that absorbs vibration, a low-rebound material that slowly recovers to its original shape over time from a compressed state can be considered.
  A groove 52 that extends in the direction of the axis O and receives the polymer material member 61 is formed in the inner wall of the speed reduction unit casing 22b. A groove 53 that extends in the direction of the axis O and receives the polymer material member 61 is formed on the outer peripheral surface of the outer pin holding portion 45.
  The polymeric material member 61 can be engaged with the grooves 52 and 53 to absorb vibrations in the rotational direction (circumferential direction) of the speed reducing portion B. Moreover, since the polymeric material member 61 engages with the grooves 52 and 53 to prevent the outer pin holding portion 45 from rotating, the detent pin 49 shown in FIG. 2 can be omitted.
  By the way, while the deceleration part B decelerates the rotation of 25 and transmits it to 28, the outer pin holding part 45 receives a reaction force in the circumferential direction from the outer pin 27. For this reason, when the cross-sectional shape of the grooves 52 and 53 is semicircular and the gap width of the annular gap 62 between the inner wall of the casing and the outer peripheral surface of the outer pin holding portion is extremely small, as shown by the arrows in FIG. The shearing force is concentrated on a part of the polymer material member 61.
  Therefore, as shown in FIG. 13, a chamfered portion 63 is formed at the boundary between the groove 52 having a semicircular cross section and the inner wall of the speed reduction portion casing 22b. The chamfered portion 63 has a bulge and smoothly connects the groove 52 and the inner wall of the casing. Thereby, it can relieve | moderate that the circumferential direction shear force concentrates on a part of member 61 made from a polymeric material.
  In addition to the rounded shape, the chamfered portion 63 may be a chamfered with a flat surface although not shown.
  Further, as shown in FIG. 13, the outer diameter of the outer pin holding part 45 is made sufficiently smaller than the inner diameter of the speed reducing part casing 22b, and the gap width of the annular gap 62 is made sufficiently large. Thereby, it can relieve | moderate that the circumferential direction shear force concentrates on a part of member 61 made from a polymeric material.
  In the present embodiment, the preferable gap width of the annular gap 62 is set to be larger than the component perpendicular to the vibration axis O of the assumed outer pin holding portion 45. Thereby, the polymeric material member 61 can efficiently absorb the vibration of the speed reducing portion B. Further, the outer pin holding portion 45 vibrates and does not come into contact with the inner wall of the speed reduction portion casing 22b, so that abnormal noise can be prevented.
  Further, the cross section of the groove 53 is formed in a V shape as shown in FIG. 13 so that the circumferential shearing force is not concentrated on a part of the polymer material member 61. Thereby, the circumferential shear force and the radial pressing force can be converted into a resultant force indicated by an arrow in FIG. Since this resultant force is a compressive force, the circumferential shear force is not concentrated on a part of the polymer material member 61, and the durability of the polymer material member 61 is improved.
  This point will be described in detail. The polymer material member 61 extends along the groove 53 having a V-shaped cross section, and has a circular cross section. Therefore, the polymer material member 61 comes into contact with the left side surface and the right side surface of the groove 53 that forms both V-shaped blades, and receives compressive force from the two contact points. Therefore, the circumferential shear force can be effectively dispersed by the combination of the V-shaped groove and the polymer material member 61 having a circular cross section.
  Although not shown, the cross-sectional shape of the groove 53 may be an arch shape. Here, the arch shape may be a parabolic curve or a catenary. Moreover, a Gothic arch shape may be sufficient. Also in the case of the arch shape, the polymer material member 61 comes into contact with the right side surface and the left side surface of the groove 53, respectively, and receives compressive force from the two contact points. Therefore, the circumferential shear force can be effectively dispersed by the combination of the groove having the cross-sectional arch shape and the member 61 made of the polymer material having the circular cross-section.
  Although not shown, a part of the plurality of polymer material members 61 provided at equal intervals in the circumferential direction may be replaced with a metal member. Reliability is improved by using a polymer material member and a metal member in combination.
  Next, a modification of the groove 53 for receiving the polymer material member 61 will be described. FIG. 14 is a longitudinal sectional view showing a modification of the present invention, and is an enlargement of the E region of FIG. In the modification shown in FIG. 14, the angle of the V-shaped groove 53 is increased. As a result, the polymer material member 61 comes into contact with the groove 53 at the center of the V shape. That is, as shown by an arrow in FIG. 14, compared to the embodiment of FIG. 13 in which the V-shaped angle is small, the input position of the pressing force can be set to the inner diameter side and away from the speed reduction unit casing 22b. The concentration of directional shear force can be further relaxed.
  Although the embodiment of the present invention has been described with reference to the drawings, the present invention is not limited to the illustrated embodiment. Various modifications and variations can be made to the illustrated embodiment within the same range or equivalent range as the present invention.
  The in-wheel motor drive device according to the present invention is advantageously used in electric vehicles and hybrid vehicles.
  21 in-wheel motor drive device, 22, 22b casing, 23 stator, 24 rotor, 25 motor side rotating member, 25a, 25b eccentric member, 26a, 26b curved plate, 27 outer pin, 28 wheel side rotating member, 31 inner pin, 32 Wheel hub, 33 Wheel hub bearing, 41 Rolling bearing, 45 Outer pin holding part, 46 Cylindrical part, 47, 48 Ring part, 49 Non-rotating pin, 51 Spring pin (metal member), 51s Slit, 52, 53 Groove, 61 Polymer material member, 62 annular gap, 63 chamfer.

Claims (15)

  1. A motor unit that rotationally drives the motor side rotating member, a speed reducing unit that decelerates the rotation of the motor side rotating member and transmits the rotation to the wheel side rotating member, and a wheel hub fixedly connected to the wheel side rotating member,
    The speed reduction part is a casing that is an outline of the speed reduction part;
    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 revolving member that has an inner periphery attached to the outer periphery of the eccentric member so as to be relatively rotatable, and performs a revolving motion around the axis along with the rotation of the input shaft;
    An outer periphery engaging member that engages with an outer peripheral portion of the revolving member to cause rotation of the revolving member;
    An output shaft for extracting the rotational motion of the revolving member;
    A ring shape centered on the axis, and an outer periphery engaging member holding portion attached to the inside of the casing and supporting the outer periphery engaging member;
    An in-wheel motor having a pressing member that is inserted between the inner wall of the casing and the outer peripheral surface of the outer peripheral engagement member holding portion while being elastically deformed and presses the outer peripheral engagement member holding portion radially inward. Drive device.
  2.   The in-wheel motor drive device according to claim 1, wherein the pressing member is a metal member made of metal.
  3.   The in-wheel motor drive device according to claim 2, wherein the metal member is inserted in at least three locations in the circumferential direction.
  4.   The in-wheel motor drive device according to claim 2, wherein the metal member is a spring pin extending in parallel with the axis.
  5.   The in-wheel motor drive device according to claim 2 or 3, wherein the metal member is a pin having a V-shaped cross section extending in parallel with the axis.
  6.   6. The in-wheel motor drive device according to claim 4, wherein an inner wall of the casing includes a recess that engages with the metal member.
  7.   The in-wheel motor drive device in any one of Claims 4-6 provided with the recessed part which the outer peripheral surface of the said outer periphery engaging member holding | maintenance part engages with the said metal members.
  8. The outer peripheral surface of the outer peripheral engagement member holding part faces the inner wall of the casing through a gap,
    The in-wheel motor drive device according to claim 1, wherein the pressing member is a polymer material member made of a polymer material.
  9.   9. The in-wheel motor drive device according to claim 8, wherein grooves are formed in the inner wall of the casing and the outer peripheral surface of the outer peripheral engagement member holding portion so as to extend in the axial direction and receive the polymer material member.
  10.   The in-wheel motor drive device according to claim 9, wherein the groove has a V-shaped cross section perpendicular to the axis.
  11.   The in-wheel motor drive device according to claim 9, wherein the groove has an arch shape in a cross section perpendicular to the axis.
  12.   The in-wheel motor according to any one of claims 9 to 11, wherein the groove has a chamfered portion at a boundary between the inner wall and the groove of the casing and a boundary between the outer peripheral surface of the outer peripheral engagement member holding portion and the groove. Drive device.
  13.   The in-wheel motor drive device according to any one of claims 10 to 12, wherein the polymer material member extends along the groove and has a circular cross-sectional shape.
  14.   The in-wheel motor drive device according to any one of claims 8 to 13, wherein the speed reduction portion further includes a metal member interposed between an inner wall of the casing and an outer peripheral surface of the outer peripheral engagement member holding portion. .
  15.   The in-wheel motor drive device according to any one of claims 8 to 14, wherein the gap is larger than a component perpendicular to an axis of vibration of the outer peripheral engagement member holding portion.
JP2009142356A 2008-08-22 2009-06-15 In-wheel motor driving device Pending JP2010071462A (en)

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JP2011226583A (en) * 2010-04-21 2011-11-10 Ntn Corp Decelerating device
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