JP2015183830A - in-wheel motor drive device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To employ an outer pin housing that facilitates installation of the inside components of a speed reducer B and facilitates working with high working accuracy even in a case where an opening part for component insertion is made small, as an outer pin housing 50 of a cycloid type speed reducer B of an in-wheel motor drive device 21.SOLUTION: An outer pin housing 50 is formed by assembling halved bodies 50a, 50b obtained by dividing the outer pin housing 50 into two parts; the components of a speed reducer B are assembled into a state of opening the halved bodies 50a, 50b; after the assembly of the components of the speed reducer B, the halved bodies 50a, 50b are closed; and assembly is completed by connecting them with a connection member 60.

Description

  The present invention relates to an outer pin housing of a cycloid reduction gear used for an in-wheel motor drive device.

  As shown in FIG. 25, the in-wheel motor drive device 121 includes a motor unit A that generates a driving force, a speed reducer B that decelerates and outputs the rotation of the motor unit A, and an output from the speed reducer B as driving wheels. And a wheel hub C to be transmitted to the vehicle.

  The motor part A and the speed reducer B are accommodated in the casing 122. The casing 122 includes a casing 122a on the motor part A side and a casing 122b on the reduction gear B side.

  The motor part A uses a radial gap type of which a stator 123 is provided on the inner peripheral surface of the casing 122a and a rotor 124 is provided at an interval on the inner periphery of the stator 123.

  The rotor 124 has a motor shaft 124a in the center. The motor shaft 124a is connected to the input shaft 130 of the speed reducer A and is inserted into the casing 122b of the speed reducer B. The bearings 125a and 125b are connected to the casing 122a. And is supported rotatably.

  The casing 122b of the speed reducer B is provided with an oil tank 141 for lubricating oil at the lower portion. The lubricating oil in the oil tank 141 is sucked by the oil pump 142, and the lubricating oil is supplied to the motor unit A and the speed reducer B for lubrication. And cooling is performed (Patent Document 1).

  An oil supply passage 143 that supplies lubricating oil to the inside of the speed reducer B extends along the inside of the casing 122a from the discharge port of the oil pump 142 that is driven by using the output rotation of the speed reducer B that decelerates the rotation of the motor unit A. And a passage extending from the rear of the casing 122a through the internal passage 144 of the motor shaft 124a and the internal passage 145 of the input shaft 130 of the speed reducer B into the casing 122b of the speed reducer B.

  The lubricating oil return passage 146 is configured by a passage that reaches the suction port of the oil pump 142 through the discharge port 147 and the oil tank 141 provided at the bottom of the casing 122b of the speed reducer B.

  As shown in FIGS. 25 to 29, the cycloid reduction gear B supports two curved plates 131 rotatably by eccentric shaft portions 130 a and 130 b provided on the input shaft 130, and these curved plates 131. Is engaged with the outer pin 132 supported on the inner side of the outer pin housing 150 located on the inner diameter surface of the casing 122b of the reduction gear B via a gap, and the input shaft 130 is rotated. The curved plate 131 is eccentrically oscillated, the rotation of the curved plate 131 is output from the output shaft 133 arranged coaxially with the input shaft 130, and the wheel hub C is rotated.

  The number of outer pins 132 supported on the inner side of the outer pin housing 150 is larger than the corrugated tooth profile 131 a on the outer periphery of the curved plate 131.

  The outer pin 132 is supported by the outer pin housing 150 located on the inner diameter surface of the casing 122b of the reduction gear B via a gap. The outer pin housing 150 is floatingly supported by floating bolts (not shown) on the outer side and the inner side with respect to the casing 122b of the speed reducer B.

  As shown in FIGS. 28 and 29, the outer pin housing 150 has a cylindrical shape having a pair of flange portions 151 on the inner diameter side of both end faces in the axial direction.

  As shown in FIG. 25, one end of the input shaft 130 is connected to the motor shaft 124a of the rotor 124 by spline fitting so as to be driven to rotate by the motor portion A, and the other end is an eccentric shaft. Parts 130a and 130b are provided.

  A pair of eccentric shaft portions 130a and 130b are provided in the axial direction of the input shaft 130, as shown in FIG. The pair of eccentric shaft portions 130a and 130b is provided such that the center of the cylindrical outer diameter surface is 180 degrees out of phase in the circumferential direction, and rolls to the outer diameter surface of each of the pair of eccentric shaft portions 130a and 130b. A bearing 134 is fitted.

  The input shaft 130 provided with the pair of eccentric shaft portions 130a and 130b is provided with a pair of counterweights 135 with a 180 ° phase shift in the circumferential direction so as to sandwich the pair of eccentric shaft portions 130a and 130b.

  As shown in FIGS. 26 and 27, the curved plate 131 is rotatably supported on the input shaft 130 by a rolling bearing 134, and the corrugated tooth profile 131a formed on the outer periphery thereof is a trochoidal curved tooth profile. As shown in FIG. 27, in the curved plate 131, a plurality of pin holes 136 are formed at equal intervals on one circle centered on the rotation axis, and each of the pair of pin holes 136 aligned in the axial direction is formed inside the curved plate 131. The pin 137 is inserted with a margin, and a part of the outer periphery of the roller bearing 137 a rotatably supported by the inner pin 137 is in contact with a part of the inner periphery of the pin hole 136.

  As shown in FIG. 26, the speed reducer B includes a curved plate 131 as a revolving member that is rotatably held by the eccentric shaft portions 130a and 130b, and a plurality of engaging teeth 131a on the outer peripheral portion of the curved plate 131. An outer pin 132, an output shaft 133 that outputs the rotation of the curved plate 131, a center collar 138 that is attached to a gap between the curved plates 131 and abuts against the end surfaces of the curved plates 131 to prevent the curved plate 131 from tilting; Is provided.

  The output shaft 133 has a flange portion 133a and a shaft portion 133b. As shown in FIGS. 26 and 27, inner pins 137 are fixed to the flange portion 133a at equal intervals on a circumference centered on the rotation axis of the output shaft 133. A wheel hub C is disposed on the outer diameter surface of the shaft portion 133b so that torque can be transmitted by serration (or spline). The flange portion 133a and the stabilizer 133d are connected via the plurality of inner pins 137, and the output shaft 133 and the stabilizer 133d rotate integrally. A pump drive shaft 133c connected to the inner rotor of the oil pump 142 is integrally provided at the end of the stabilizer 133d on the motor part A side.

  As shown in FIG. 27, the outer pins 132 are provided at equal intervals on the circumferential track of the rotation axis of the input shaft 130. When the curved plate 131 revolves, the corrugated tooth profile 131a on the outer periphery engages with the outer pin 132 to cause the curved plate 131 to rotate.

  As shown in FIG. 26, an output shaft 133 and a stabilizer 133 d are rotatably supported via a bearing 190 on the inner periphery of the flange portion 151 of the outer pin housing 150. An inner diameter surface of the flange portion 133a and the stabilizer 133d of the output shaft 133 and an outer diameter surface of the input shaft 130 are supported through a bearing 191 so as to be relatively rotatable.

The curved plate 131 is incorporated between the flange portion 133a and the stabilizer 133d facing the output shaft 133. Further, both ends of the inner pin 137 penetrating the pin hole 136 of the curved plate 131 are supported by the flange portion 133a and the stabilizer 133d facing the output shaft 133.
The plurality of inner pins 137 supported by the flange portion 133 a and the stabilizer 133 d facing the output shaft 133 are provided at equal intervals on a circumferential track centering on the rotation axis of the input shaft 130, and friction with the curved plate 131. In order to reduce the resistance, a needle roller bearing 137a is provided at a position where it abuts against the inner wall surface of the pin hole 136 of the curved plate 131. The inner diameter dimension of the pin hole 136 is set larger than the outer diameter dimension of the inner pin 37 by a predetermined amount.

  As shown in FIG. 25, the wheel hub C includes an inner ring member 181 fitted and connected to the outer diameter surface of the shaft portion 133b of the output shaft 133 so that torque can be transmitted by serration (or spline), and an inner ring member 181. And an outer ring member 182 that is rotatably held with respect to the casing 122b. The inner ring member 181 and the outer ring member 182 constitute a double row angular ball bearing, and a double row rolling element 183 is installed between the inner ring member 181 and the outer ring member 182. The inner ring member 181 is integrally provided with a wheel mounting flange portion 184.

  The outer pin 132 is not directly held by the casing 122b, but is held by an outer pin housing 150 supported in a floating state on the inner diameter surface of the casing 122b, as shown in FIG.

  Further, as shown in FIGS. 28 and 29, a slit 153 is provided at the lower part of the cylindrical outer pin housing 150.

  The pair of flange portions 151 of the outer pin housing 150 are provided with a plurality of outer pin holding holes 154 penetrating in the thickness direction. As shown in FIG. 26, the outer pin holding holes 154 extend in a direction parallel to the rotation axis of the input shaft 130 and hold both ends of the outer pin 132. Both ends of the outer pin 132 are supported by the outer pin holding hole 154 via needle roller bearings 155. The needle roller bearing 155 includes an outer ring 155a and needle rollers 155b having the inner peripheral surface of the outer ring 155a and the outer peripheral surface of the outer pin 132 as rolling surfaces. The outer ring 155 a of the needle roller bearing 155 is fitted to the inner surface of the outer pin holding hole 154.

  Further, the corresponding outer pin holding holes 154 of the pair of flange portions 151 are provided at the same position in the circumferential direction so as to face each other. That is, the central axes of the pair of outer pin holding holes 154 coincide with each other, and when the outer pin housing 150 is attached to the casing 122b of the speed reducer B, the central axis of the outer pin holding holes 154 becomes the rotation axis of the input shaft 130. Become parallel.

  As shown in FIG. 28, a thick portion is formed on the inner diameter side of the pair of flange portions 151. A groove-shaped counterbore 157 is formed on the outer diameter surface of the thick portion so as to be continuous with the outer pin holding hole 154.

  As shown in FIG. 26, an outer pin side plate 158 that prevents the outer pin 132 inserted into the outer pin holding hole 154 from coming out in the axial direction is formed on the outer side surface portion located on the radially outer peripheral side of the pair of flange portions 151. Is fixed.

JP 2012-97903 A

  Incidentally, the cylindrical outer pin housing 150 of the cycloid reduction gear B is integrally formed by boring as shown in FIGS.

  Since the outer pin housing 150 is large in size and complicated in internal shape, it is difficult to process and the manufacturing cost is high.

  Further, when cutting the inside of the cylindrical outer pin housing 150, it is difficult to improve the machining accuracy because the protruding amount of the tool must be increased.

  When assembling the reducer B, the outer pin housing 150 is integrally formed. Therefore, internal components such as the curved plate 131 are inserted into the outer pin housing 150 through the slit 153, and the inner portion of the outer pin housing 150 is inserted. Must be assembled in. For this reason, it takes time to assemble the reduction gear B, and it is necessary to open a slit 153 for inserting the internal parts in the outer pin housing 150 so that large components such as the curved plate 131 can be inserted inside. In some cases, the strength of the outer pin housing 150 may be reduced by the large slit 153.

  Accordingly, the present invention is intended to provide an outer pin housing that can incorporate the internal parts of the speed reducer even if the opening for inserting the parts is small, is easy to process, and has high processing accuracy.

  In order to solve the above problems, in the present invention, a motor unit that generates a driving force, a speed reducer that decelerates and outputs the rotation of the motor unit, and a wheel hub that transmits the output from the speed reducer to the drive wheels. An input shaft that is rotationally driven by the motor unit, a curved plate that is rotatably supported on the input shaft by an eccentric shaft portion provided on the input shaft, and has a corrugated tooth profile formed on the outer periphery; An outer pin that meshes with the corrugated tooth profile on the outer periphery of the curved plate, and a cylindrical outer pin that is provided in a state of being prevented from rotating on the inner diameter surface of the casing of the speed reducer and that has flange portions that support both end portions of the outer pin on both end surfaces A curved plate is incorporated in the outer pin housing, and the curved plate is eccentrically oscillated by rotation of the input shaft, and rotation of the curved plate is performed from an output shaft arranged coaxially with the input shaft. Output In the in-wheel motor drive device that is an Icroid type speed reducer, the outer pin housing is formed by assembling a half-divided body, and the components of the speed reducer are assembled in a state in which the half-divided body is opened. The halved body incorporating the reduction gear component is closed and connected by a connecting member.

  The split surface of the half-divided body may be orthogonal or inclined with respect to the axis of the speed reducer.

  As the connecting member, a clip fitted on the outer peripheral surface of the two halves closed together can be used.

  At both ends of the clip, there are provided leg portions that overlap both side surfaces of the two halves closed together, and an engaging portion is provided between the leg portions of the clip and both side surfaces of the two halves. The connection strength of the two halves closed together can be improved.

  A plurality of the clips are provided at equal intervals in the circumferential direction of the outer peripheral surface of the two halves closed together, and the legs overlapped on both side surfaces of the two halves closed together provided at both ends of the clip, By connecting at least the leg portion that overlaps one side surface of the half-divided body by an annular ring member, the connection strength of the two halves closed together can be improved.

  As the connecting member, a connecting shaft inserted in a plurality of through-holes penetrating in the axial direction provided in two closed halves can be used.

  By providing a head for retaining at one end of the connecting shaft and fitting a retaining ring at the other end, the connecting shaft can be prevented from coming off from the half body.

  An outer pin thrust plate can be fitted between the head of the connecting shaft and the outer surface of the half body, and between the retaining ring of the connecting shaft and the outer surface of the half body.

  By providing a shaft that passes through the two halves that are closed together, it is possible to receive a torsional stress applied to the two halves.

  In the in-wheel motor drive device according to the present invention, as described above, since the outer pin housing is formed by assembling the half-divided body, the machining is easy and the machining accuracy is high. In addition, since the internal parts of the speed reducer can be assembled into the outer pin housing with the two-part halves opened, the work of assembling the internal parts of the speed reducer is easy. Further, the opening for inserting the component can be made small, and the strength of the outer pin housing can be improved.

It is a vertical front view of the in-wheel motor drive device concerning this invention. It is an expansion vertical front view of a reduction gear. It is a vertical side view along the DD line of FIG. It is an enlarged view of an oil pump. It is a disassembled perspective view which shows an example of an outer pin housing. It is a perspective view which shows the state which closes the half body which forms the outer pin housing of FIG. 5, and fits the clip of a connection member. It is a perspective view which shows the state which closed the half body which forms the outer pin housing of FIG. 5, and fitted the clip of the connection member. It is a longitudinal cross-sectional view of FIG. It is an exploded view which shows the assembly procedure of the reduction gear which uses the outer pin housing of FIG. (A) (b) (c) (d) is an enlarged view of the circled portion of FIG. 8 showing a coupling example of the clip of the connecting member and the outer pin housing. It is a disassembled perspective view of the outer pin housing which uses another example of the clip of a connection member. It is a perspective view which shows the state which closed the half member which forms an outer pin housing from the state of FIG. It is a perspective view which shows the state which assembled the outer pin housing of FIG. It is a front view which shows the state which assembled the outer pin housing of FIG. It is an expanded view of the board of the spring steel which produces another example of the clip of a connection member. It is a perspective view which shows the state before bending the board of FIG. 15 and connecting an annular member. It is a perspective view which shows the state which connected the annular member from the state of FIG. It is an enlarged view of the connection part of the annular member of FIG. It is a vertical front view of the in-wheel motor drive device based on this invention using the shaft which receives the torsional force of the mating surface of a half-divided body. It is an expansion vertical front view of the reduction gear which uses a connection shaft as a connection member. It is an enlarged view of the connection shaft part of FIG. It is an enlarged view which shows another example of a connection shaft. It is a schematic plan view of the electric vehicle which has the in-wheel motor drive device of FIG. It is the figure which looked at the electric vehicle of FIG. 23 from back. It is a vertical front view which shows a prior art example. It is an expansion vertical front view of the reduction gear of a prior art example. It is a vertical side view along the DD line of FIG. It is a perspective view of the conventional outer pin housing. It is a longitudinal cross-sectional view of the conventional outer pin housing.

Embodiments of the present invention will be described below with reference to the accompanying drawings.
As shown in FIG. 23, an electric vehicle 11 including an in-wheel motor drive device according to an embodiment of the present invention includes a chassis 12, front wheels 13 as steering wheels, drive wheels (rear wheels) 14, left and right And an in-wheel motor drive device 21 that transmits a drive force to each of the drive wheels 14. As shown in FIG. 24, the drive wheel 14 is accommodated in a wheel housing 12a of the chassis 12, and is fixed to the lower portion of the chassis 12 via a suspension device (suspension) 12b. As a mounting form of the in-wheel motor drive device 21, in addition to the rear-wheel drive system shown in FIGS.

  The suspension device 12b supports the drive wheel 14 by a suspension arm that extends to the left and right, and suppresses vibration of the chassis 12 by absorbing vibration received by the drive wheel 14 from the ground by a strut including a coil spring and a shock absorber. Furthermore, a stabilizer that suppresses the inclination of the vehicle body when turning or the like is provided at a connecting portion of the left and right suspension arms. The suspension device 12b is an independent suspension type in which the left and right wheels can be moved up and down independently in order to improve the followability to the road surface unevenness and efficiently transmit the driving force of the driving wheels to the road surface. Is desirable.

  The electric vehicle 11 needs to be provided with a motor, a drive shaft, a differential gear mechanism, and the like on the chassis 12 by providing an in-wheel motor drive device 21 that drives the left and right drive wheels 14 inside the wheel housing 12a. This eliminates the need to secure a wide cabin space and control the rotation of the left and right drive wheels.

  As shown in FIG. 1, the in-wheel motor drive device 21 includes a motor unit A that generates a driving force, a speed reducer B that decelerates and outputs the rotation of the motor unit A, and an output from the speed reducer B as driving wheels. The motor hub A and the speed reducer B are housed in the casing 22 and are mounted in the wheel housing 12a of the electric vehicle 11 as shown in FIG.

  The motor part A and the speed reducer B are accommodated in the casing 22. The casing 22 includes a casing 22a on the motor part A side and a casing 22b on the reduction gear B side.

  The motor part A uses a radial gap type in which a stator 23 is provided on the inner peripheral surface of the casing 22a, and a rotor 24 is provided at an interval on the inner periphery of the stator 23.

  The rotor 24 has a motor shaft 24a at the center, and the motor shaft 24a is connected to the input shaft 30 of the speed reducer B and is inserted into the casing 22b of the speed reducer B. And is supported rotatably.

  The casing 22b of the speed reducer B is provided with an oil tank 41 for lubricating oil at the lower portion, the lubricating oil in the oil tank 41 is sucked by the oil pump 42, and the lubricating oil is supplied to the motor unit A and the speed reducing device B for lubrication. And cooling.

  The oil supply passage 43 that supplies lubricating oil to the inside of the speed reducer B extends along the inside of the casing 22a from the discharge port of the oil pump 42 that is driven by using the output rotation of the speed reducer B that decelerates the rotation of the motor part A. The passage extends from the rear of the casing 22a through the internal passage 44 of the motor shaft 24a and the internal passage 45 of the input shaft 30 of the reduction gear B to the inside of the casing 22b of the reduction gear B. The lubricating oil supplied from the oil pump 42 is scattered by the centrifugal force and the pressure of the oil pump 42 from the radial supply port provided in the internal passage 45 of the input shaft 30 of the speed reducer B, and the speed reducer B The inside is lubricated and cooled. A so-called axial center lubrication system is adopted.

  The return passage 46 for the lubricating oil is constituted by a discharge port 47 provided at the bottom of the casing 22 b of the speed reducer B and a passage that reaches the suction port of the oil pump 42 through the oil tank 41.

  As shown in FIG. 4, the oil pump 42 includes an inner rotor 72 that rotates using the rotation of the speed reducer B, an outer rotor 73 that rotates following the rotation of the inner rotor 72, a pump chamber 74, and a feedback The cycloid pump includes a suction port 75 communicating with the passage 46 and a discharge port 76 communicating with the oil supply passage 43.

  Inner rotor 72 has a tooth profile formed of a cycloid curve on the outer diameter surface. Specifically, the shape of the tooth tip portion 72a is an epicycloid curve, and the shape of the tooth gap portion 72b is a hypocycloid curve. The inner rotor 72 rotates integrally with the output shaft 33 of the speed reducer B.

  The outer rotor 73 has a tooth profile formed of a cycloid curve on the inner diameter surface. Specifically, the shape of the tooth tip portion 73a is a hypocycloid curve, and the shape of the tooth gap portion 73b is an epicycloid curve. The outer rotor 73 is rotatably supported by the pump case 77.

  The inner rotor 72 rotates around the rotation center c1. On the other hand, the outer rotor 73 rotates around a rotation center c2 different from the rotation center c1 of the inner rotor 72. Further, when the number of teeth of the inner rotor 72 is n, the number of teeth of the outer rotor 73 is (n + 1). In this embodiment, n = 5.

  A plurality of pump chambers 74 are provided in the space between the inner rotor 72 and the outer rotor 73. When the inner rotor 72 rotates using the rotation of the output shaft 33 of the speed reducer B, the outer rotor 73 rotates in a driven manner. At this time, since the inner rotor 72 and the outer rotor 73 rotate around different rotation centers c1 and c2, the volume of the pump chamber 74 continuously changes. As a result, the lubricating oil flowing in from the suction port 75 is pumped from the discharge port 76 to the oil supply passage 43.

  As shown in FIG. 1, the casing 22 b of the speed reducer B is provided with an oil tank 41 for lubricating oil at the lower portion. The lubricating oil in the oil tank 41 is sucked by the oil pump 42 through the return passage 46, and the motor unit A Lubricating oil is supplied to the reduction gear B to perform lubrication and cooling.

  As shown in FIGS. 1 to 3, the cycloid type speed reducer B rotatably supports two curved plates 31 by eccentric shaft portions 30 a and 30 b provided on the input shaft 30, and these curved plates 31. The corrugated tooth profile 31a formed on the outer periphery of the gear plate is engaged with the outer pin 32 disposed inside the casing 22b of the speed reducer B, and the curved plate 31 is caused to eccentrically swing by the rotation of the input shaft 30. The rotation of 31 is output from the output shaft 33 arranged coaxially with the input shaft 30, and the wheel hub C is rotated.

  The number of outer pins 32 disposed inside the casing 22 b of the reduction gear B is larger than the corrugated tooth profile 31 a on the outer periphery of the curved plate 31.

  As shown in FIG. 1, the outer pin 32 is supported by an outer pin housing 50 that is disposed on the inner diameter surface of the casing 22 b of the speed reducer B via a gap. The outer pin housing 50 is floatingly supported by floating bolts (not shown) on the outer side and the inner side with respect to the casing 22b of the speed reducer B.

  As shown in FIGS. 5 to 8, the outer pin housing 50 is composed of two divided halves 50 a and 50 b, and the two divided halves 50 a and 50 b are combined on the dividing surface to connect the connecting members 60. Are assembled together.

  The outer pin housing 50 shown in FIGS. 5 to 8 is an example in which the split surfaces of the halves 50a and 50b are provided so as to be orthogonal to the axis of the speed reducer B. These dividing surfaces may not be orthogonal to the axis of the speed reducer B, may be inclined, or may be parallel to the axis of the speed reducer B.

  The outer pin housing 50 has a cylindrical shape in a state in which the split surfaces of the halves 50a and 50b are combined and connected by the connecting member 60, and includes a pair of flange portions 51 that extend to the inner diameter side at both ends in the axial direction.

  As shown in FIG. 1, one end of the input shaft 30 is connected to the motor shaft 24a of the rotor 24 by spline fitting and is driven to rotate by the motor portion A. The other end is an eccentric shaft. Portions 30a and 30b are provided.

  As shown in FIG. 2, a pair of eccentric shaft portions 30 a and 30 b are provided in the axial direction of the input shaft 30. The pair of eccentric shaft portions 30a and 30b is provided such that the center of the cylindrical outer diameter surface is 180 degrees out of phase in the circumferential direction, and rolls to the outer diameter surface of each of the pair of eccentric shaft portions 30a and 30b. A bearing 34 is fitted.

  The input shaft 30 provided with the pair of eccentric shaft portions 30a and 30b is provided with a pair of counterweights 35 with a 180 ° phase shift in the circumferential direction so as to sandwich the pair of eccentric shaft portions 30a and 30b.

  The curved plate 31 is rotatably supported on the input shaft 30 by the rolling bearing 34, and the corrugated tooth profile 31a formed on the outer periphery thereof is a trochoidal curved tooth profile. As shown in FIG. 3, the curved plate 31 has a plurality of pin holes 36 formed at equal intervals on a single circle centered on the rotation axis, and each of the pair of pin holes 36 aligned in the axial direction is formed inside each of the pin holes 36. The pin 37 is inserted with a margin, and a part of the outer periphery of the roller bearing 37 a rotatably supported by the inner pin 37 is in contact with a part of the inner periphery of the pin hole 36.

  As shown in FIG. 2, the speed reducer B is engaged with two curved plates 31 as revolving members that are rotatably held by the eccentric shaft portions 30 a and 30 b, and a corrugated tooth profile 31 a on the outer peripheral portion of the curved plate 31. A plurality of outer pins 32, an output shaft 33 that outputs the rotational movement of the curved plate 31, and a gap between the two curved plates 31 are in contact with the end surfaces of the curved plates 31 to prevent the curved plate from tilting. And a center collar 38.

  The output shaft 33 has a flange portion 33a and a shaft portion 33b. As shown in FIG. 3, inner pins 37 are fixed to the flange portion 33 a at equal intervals on a circumference centered on the rotation axis of the output shaft 33. As shown in FIG. 1, a wheel hub C is provided on the outer diameter surface of the shaft portion 33b so that torque can be transmitted by serrations (or splines). The flange portion 33a and the stabilizer 33d are connected via the plurality of inner pins 37, and the output shaft 33 and the stabilizer 33d rotate integrally. A pump drive shaft 33c connected to the inner rotor 72 of the oil pump 42 is integrally provided at the end of the stabilizer 33d on the motor part A side.

  The outer pins 32 are provided at equal intervals on the circumferential track of the rotation axis of the input shaft 30. When the curved plate 31 revolves, the outer peripheral corrugated tooth profile 31a and the outer pin 32 engage with each other, causing the curved plate 31 to rotate.

  As shown in FIG. 2, the output shaft 33 is rotatably supported via a bearing 90 on the flange portion 51 of the outer pin housing 50 and the inner periphery of the stabilizer 33 d. Further, the inner diameter surface of the flange portion 33 a and the stabilizer 33 d of the output shaft 33 and the outer diameter surface of the input shaft 30 are supported through a bearing 91 so as to be relatively rotatable.

  The curved plate 31 is incorporated between the flange portion 33a and the stabilizer 33d facing the output shaft 33. Further, both ends of the inner pin 37 penetrating the pin hole 36 of the incorporated curved plate 31 are supported by the flange portion 33 a facing the output shaft 33.

  The plurality of inner pins 37 supported by the flange portion 33 a and the stabilizer 33 d that face the output shaft 33 are provided at equal intervals on a circumferential track centering on the rotational axis of the input shaft 30, and friction with the curved plate 31. In order to reduce the resistance, needle roller bearings 37a are provided at positions where they contact the inner wall surfaces of the pin holes 36 of the two curved plates 31. The inner diameter dimension of the pin hole 36 is set to be larger than the outer diameter dimension of the inner pin 37 (referred to as “maximum outer diameter including the needle roller bearing 37a”; the same applies hereinafter).

  As shown in FIG. 9, the speed reducer B has an input shaft 30, two curved plates 31, a counter weight 35, an output shaft in a state in which the halves 50a and 50b of the divided outer pin housing 50 are opened. 33, the inner parts of the reduction gear B incorporated in the outer pin housing 50 such as the inner pin 37 and the rolling bearings 90 and 91 are assembled, and then the outer ring 55a and the needle roller 55b of the needle roller bearing 55 are assembled. The halves 50a and 50b are formed by two halves 50a and 50b by sandwiching the internal parts of the speed reducer B from the left and right, and then inserting the outer pin 32 and attaching the outer pin side plate 58 to the end face. Assembling is completed by attaching clip-type connecting members 60 at several locations on the outer peripheral surface of the cylindrical portion.

  Thus, since the internal parts of the reduction gear B can be assembled with the halves 50a and 50b of the outer pin housing 50 divided into two parts open, the halves 50a of the outer pin housing 50 can be assembled. The opening provided in 50b only needs to be large enough to allow the input shaft 30 and the output shaft 33 to be inserted therethrough. Therefore, since the opening part of the magnitude | size which inserts the big curve board 31 in the outer pin housing 50 becomes unnecessary, the intensity | strength of the outer pin housing 50 improves.

  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 housing 50, which requires high strength, from steel.

  As shown in FIGS. 5 to 8, the outer pin housing 50 formed by the halves 50a and 50b is a cylindrical type including a pair of flange portions 51 extending radially inward from both axial end portions. The pair of flange portions 51 has a thick portion on the inner diameter side of the outer surface portion.

  Further, around the outer pin housing 50, several cutouts 53 for removing the lubricating oil in the outer pin housing 50 are provided on the mating surfaces of the halves 50a and 50b (see FIGS. 5 and 6). In addition, fixing holes 59 for floating bolts are provided at equal intervals in the circumferential direction on the outer side surfaces of the halves 50a and 50b.

  As shown in FIG. 2, a plurality of outer pin holding holes 54 penetrating in the thickness direction are provided in a pair of flange portions 51 of the outer pin housing 50 formed by combining the halves 50a and 50b. The outer pin holding holes 54 extend in a direction parallel to the rotation axis of the input shaft 30 and hold both ends of the outer pin 32. Both ends of the outer pin 32 are supported by the outer pin holding hole 54 via needle roller bearings 55. The needle roller bearing 55 includes an outer ring 55a and needle rollers 55b having an inner peripheral surface of the outer ring 55a and an outer peripheral surface of the outer pin 32 as rolling surfaces. The outer ring 55 a of the needle roller bearing 55 is fitted into the inner surface of the outer pin holding hole 54.

  Further, the corresponding outer pin holding holes 54 of the pair of flange portions 51 are provided so as to face each other at the same position in the circumferential direction. That is, the center axes of the pair of outer pin holding holes 54 coincide with each other, and when the outer pin housing 50 is attached to the casing 22 b of the reduction gear B, the center axis of the outer pin holding holes 54 is parallel to the rotation axis of the input shaft 30. become. Thereby, the outer pin 32 can be held in parallel with the rotation axis of the input shaft 30.

  As shown in FIG. 5 to FIG. 8, a groove-shaped counterbore portion 57 is formed in the thick portion located on the radially inner peripheral side of the pair of flange portions 51 so as to be continuous with the outer pin holding hole 54. Has been.

  As shown in FIGS. 2 and 9, an outer pin that prevents the outer pin 32 inserted in the outer pin holding hole 54 from coming out in the axial direction is provided on the outer side surface portion located on the outer peripheral side in the radial direction of the pair of flange portions 51. The side plates 58 are fixed respectively.

  The outer pin housing 50 of the embodiment shown in FIGS. 5 to 9 uses a metal press product as the connecting member 60 of the halves 50a and 50b. Here, the outer pin housing 50 has a U-shape formed by press forming of spring steel. A clip 61 is used.

  By fitting the clip 61 to the outer peripheral surfaces of the combined halves 50a and 50b, separation of the combined halves 50a and 50b in the axial direction can be prevented.

  When the outer pin housing 50 is formed by combining the halves 50a and 50b, a twisting force is applied to the mating surfaces of the halves 50a and 50b by torque load.

  In order to receive the twisting force of the mating surfaces of the halves 50a and 50b, it is desirable to provide positioning irregularities or a plurality of pins that fit together on the mating surfaces of the halves 50a and 50b.

  Further, when a U-shaped clip 61 is used as the connecting member 60, in order to improve the connection strength between the clip 61 and the half-split members 50a, 50b by receiving the twisting force of the mating surfaces of the half-split members 50a, 50b. As shown in FIGS. 10A to 10D, engaging portions 62 are provided on the overlapping surfaces of the leg portions 61a at both ends of the clip 61 and the flange portions 51 of the halves 50a and 50b. 10A to 10D illustrate a plurality of types of engaging portions 62 on the half-divided body 50a side by enlarging the circled portion in FIG. 8, but the half-divided body 50b side is also illustrated. Each type has the same configuration.

  10 (a) is provided with inwardly bent portions 61b at the tips of the leg portions 61a at both ends of the clip 61, and a concave portion 61c into which the bent portion 61b is fitted is a flange portion of the halves 50a and 50b. It is an example provided on the side surface of 51.

  The engaging portion 62 in FIG. 10B is provided with a curved bent portion 61d having an inward spring force at the tip of the leg portion 61a at both ends of the clip 61, and a concave portion 61e into which the bent portion 61d is fitted is divided in half. It is an example provided on the side surface of the ring portion 52 of 50a and 50b.

  10C is an example in which convex portions 61f with which both end surfaces of the leg portions 61a of the clip 61 abut are provided on the side surfaces of the ring portions 52 of the halves 50a and 50b.

  10 (d) is an example in which a convex portion 61g is provided on the side surface of the flange portion 51 of the halves 50a and 50b, and a concave portion 61h into which the convex portion 61g is fitted is provided in the leg portion 61a of the clip 61. It is.

  Next, in the embodiment shown in FIGS. 11 to 18, another type of clip 63 (connection member 60) is used as the connection member 60 of the halves 50 a and 50 b.

  The clip 63 extends in the axial direction in which the annular member 63a fitted to the thick inner side surface 52b of the flange portion 51 of one half member 50a and the half members 50a and 50b are combined from the annular member 63a. It consists of four clip parts 63b.

  The annular member 63a and the four clip parts 63b are made of a metal press product, and here are integrally formed by pressing with spring steel.

  The clip part 63b has bent pieces 63c that fit on both side surfaces of the combined halves 50a and 50b. The bent piece 63c is curved inward so as to be elastically fitted to both side surfaces of the flange portions 51 of the combined halves 50a and 50b.

  15 to 18 show an embodiment in which the clip 63 is formed by bending a spring steel plate.

  In the embodiment of FIGS. 15 to 18, the band member that forms the annular member 63 a and the clip piece that forms the clip portion 63 b are integrally formed by press punching.

  A caulking portion 63e is provided at one end of the band member forming the annular member 63a, and an engagement hole 63d into which the caulking portion 63e is inserted is provided at the other end of the band member. As shown in FIG. 16, the band member forming the annular member 63a is bent in an annular shape so that one end and the other end overlap each other, and the caulking portion 63e at one end is inserted into the engagement hole 63d at the other end. And as shown in FIG. 18, the annular member 63a can be formed by bending the crimp part 63e.

  Next, in the embodiment shown in FIG. 19, when the outer pin housing 50 is formed by combining the halves 50a and 50b, as described above, a twisting force is applied to the mating surfaces of the halves 50a and 50b by the torque load. Therefore, the shaft 64 penetrating the halves 50a and 50b is inserted into the halves 50a and 50b so as to receive this twisting force. In the embodiment shown in FIG. 19, a U-shaped clip 61 formed by spring steel press molding is used as the connecting member 60 of the halves 50a, 50b.

  Next, the embodiment shown in FIGS. 20 to 22 is an example in which a connecting shaft 65 is used as the connecting member 60 of the halves 50a and 50b.

  In the combined halves 50a and 50b, a through hole 66 through which the connecting shaft 65 is inserted is formed in the axial direction.

  The connecting shaft 65 is formed longer than the combined width of the halves 50a and 50b and the thickness of the outer pin side plate 58.

  The connecting shaft 65 of FIGS. 20 and 21 is provided with a head 65a for retaining at one end, and halves 50a and 50b each having a retaining ring 65b fitted and connected to the tip of the connecting shaft 65 are connected. .

  Further, the connecting shaft 65 shown in FIG. 22 has a retaining pin 65c inserted into a retaining hole at the tip, and connects the combined halves 50a and 50b. A spring washer 65d is fitted between the head of the connecting shaft 65 shown in FIG. 22 and the outer pin side plate 58 to prevent the connecting shaft 65 from rattling.

  In the embodiment using the connecting shaft 65 shown in FIGS. 20 to 22, a plurality of connecting shafts 65 are installed at equal intervals in the circumferential direction. The relationship between the connecting shaft 65 and the through holes 66 provided in the halves 50a and 50b is preferably a clearance fit. However, the position accuracy of the combined halves 50a and 50b can be improved by using several tight fits. Can be improved.

  As shown in FIG. 1, the wheel hub C includes an inner ring member 81 fixedly connected to the outer diameter surface of the shaft portion 33b of the output shaft 33, and an outer ring member 82 that rotatably holds the inner ring member 81 with respect to the casing 22b. With. The inner ring member 81 and the outer ring member 82 constitute a double-row angular ball bearing, and a double-row rolling element 83 is installed between the inner ring member 81 and the outer ring member 82. The inner ring member 81 is integrally provided with a wheel mounting flange portion 84.

  In the above-described embodiment, an example of a cylindrical roller bearing has been shown as the rolling bearing 34 that supports the curved plate 31. However, the present invention is not limited to this example. 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.

  Moreover, in the said embodiment, the radial gap provided with the stator 23 fixed to the casing 22a in the motor part A, and the rotor 24 arrange | positioned in the position which faces the inner side of the stator 23 with a radial gap. Although the example which employ | adopted the motor was shown, the motor of arbitrary structures is applicable, without restricting to this. 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 equipped with the in-wheel motor drive device 21 according to the present invention may have the rear wheels as drive wheels, the front wheels as drive wheels, 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.

11: Electric vehicle 12: Chassis 12a: Wheel housing 12b: Suspension device 13: Front wheel 14: Drive wheel 21: In-wheel motor drive device 22: Casing 22a: Casing 22b: Casing 23: Stator 24: Rotor 24a: Motor shaft 25a: Bearing 25b: Bearing 30: Input shaft 30a: Eccentric shaft portion 30b: Eccentric shaft portion 31: Curved plate 31a: Corrugated tooth profile 32: Outer pin 33: Output shaft 33a: Flange portion 33b: Shaft portion 33c: Pump drive shaft 34: Rolling Bearing 35: Counter weight 36: Pin hole 37: Inner pin 37a: Bearing 38: Center collar 41: Oil tank 42: Oil pump 43: Oil supply passage 44: Internal passage 45: Internal passage 46: Return passage 47: Discharge port 50: Outer pin housing 50a: Half body 50b: Half Body 51: Flange 52: Ring 52b: Inner side 53: Notch 54: Outer pin holding hole 55: Bearing 55a: Outer ring 57: Counterbore 58: Outer pin side plate 59: Fixing hole 60: Connecting member 61: Clip 61a: leg portion 61b: bent portion 61c: recessed portion 61d: bent portion 61e: recessed portion 61f: protruding portion 61g: protruding portion 61h: recessed portion 62: engaging portion 63: clip 63a: annular member 63b: clip portion 63c: bent piece 63d: engagement hole 63e: caulking portion 64: shaft 65: coupling shaft 65a: head 65b: retaining ring 65c: retaining pin 65d: spring washer 66: through hole 72: inner rotor 72a: tooth tip portion 72b: tooth groove Part 73: Outer rotor 73a: Tooth tip part 73b: Tooth gap part 74: Pump chamber 75: Suction port 76: Discharge port 77 Pump casing 81: inner ring member 82: outer ring member 83: rolling element 84: a wheel mounting flange portion 90: Bearing 91: Bearing A: Motor unit B: reducer C: wheel hub c1: rotation center c2: rotation center

Claims (10)

  A motor unit that generates a driving force, a speed reducer that decelerates and outputs the rotation of the motor unit, and a wheel hub that transmits the output from the speed reducer to a drive wheel, and the speed reducer is rotationally driven by the motor unit. An input shaft, a curved plate that is rotatably supported by the input shaft by an eccentric shaft portion provided on the input shaft, and has a corrugated tooth profile formed on the outer periphery, and an outer pin that meshes with the corrugated tooth profile on the outer periphery of the curved plate, A cylindrical outer pin housing that is provided in a state of being prevented from rotating on the inner diameter surface of the casing of the speed reducer and has flange portions that support both end portions of the outer pin at both end surfaces, and a curved plate in the outer pin housing The cycloid-type speed reducer is configured such that the curved plate is eccentrically oscillated by the rotation of the input shaft, and the rotation of the curved plate is output from the output shaft arranged coaxially with the input shaft. In-wheel mode In the driving device, the outer pin housing is formed by assembling a half-divided body, and the components of the speed reducer are assembled with the half-divided body open, and the components of the speed reducer are incorporated. The in-wheel motor drive device characterized by closing and connecting with a connection member.   The in-wheel motor drive device according to claim 1, wherein the split surface of the half-divided body is orthogonal to the axis of the speed reducer.   The in-wheel motor drive device according to claim 2, wherein the connecting member includes a clip that fits on the outer peripheral surfaces of the two halves closed together.   Legs that overlap both sides of the two halves closed together were provided at both ends of the clip, and engaging portions were provided between the legs of the clip and both sides of the two halves. The in-wheel motor drive device of Claim 3 characterized by these.   A plurality of the clips are provided at equal intervals in the circumferential direction of the outer peripheral surface of the two halves closed together, and the legs overlapped on both side surfaces of the two halves closed together provided at both ends of the clip, The in-wheel motor drive device according to claim 3 or 4, wherein the leg portions overlapping at least one side surface of the half-divided body are connected by an annular ring member.   3. The in-wheel motor drive device according to claim 2, wherein the connecting member is a connecting shaft that is inserted into a plurality of through-holes penetrating in the axial direction provided in two closed halves.   7. The in-wheel motor drive device according to claim 6, wherein a head for preventing the connection shaft is provided at one end of the connection shaft, and a connection ring is fitted at the other end to prevent the connection shaft from being detached from the half body.   7. An outer pin thrust plate is fitted between the head of the connecting shaft and the outer surface of the half body, and between the retaining ring of the connecting shaft and the outer surface of the half body. Or the in-wheel motor drive device of 7.   The in-wheel motor drive device according to any one of claims 6 to 8, wherein an elastic member is disposed on an axis of the connecting shaft to eliminate axial backlash.   The in-wheel motor drive device according to any one of claims 1 to 9, wherein a shaft that penetrates the two halves that are closed together is provided.

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