WO2020183815A1 - Power transmission device - Google Patents

Power transmission device Download PDF

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Publication number
WO2020183815A1
WO2020183815A1 PCT/JP2019/047106 JP2019047106W WO2020183815A1 WO 2020183815 A1 WO2020183815 A1 WO 2020183815A1 JP 2019047106 W JP2019047106 W JP 2019047106W WO 2020183815 A1 WO2020183815 A1 WO 2020183815A1
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WO
WIPO (PCT)
Prior art keywords
shaft
motor
gear
power transmission
hollow shaft
Prior art date
Application number
PCT/JP2019/047106
Other languages
French (fr)
Japanese (ja)
Inventor
松尾　浩司
Original Assignee
ジヤトコ株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ジヤトコ株式会社 filed Critical ジヤトコ株式会社
Publication of WO2020183815A1 publication Critical patent/WO2020183815A1/en

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K1/00—Arrangement or mounting of electrical propulsion units
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/16—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of differential gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/38—Constructional details
    • F16H48/40—Constructional details characterised by features of the rotating cases
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/12—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of electric gearing

Definitions

  • the present invention relates to a power transmission device.
  • Patent Documents 1 to 3 disclose a power transmission device.
  • the rotor of the motor is a hollow shaft, and the drive shaft penetrates the inside of the hollow shaft. Therefore, it is possible to reduce the size in the vertical direction compared to the 3-axis type, but because a large counter gear is arranged, the size is increased in the vertical direction (hereinafter referred to as the 2-axis type). ..
  • the power transmission device of Patent Document 3 uses a planetary reduction gear having a stepped pinion instead of a counter gear, and can be downsized in the vertical direction as compared with the 2-axis type (hereinafter referred to as the 1-axis type). I will call it).
  • the two-axis type and one-axis type power transmission devices can be reduced in size in the vertical direction (gravity direction), but there is a problem in reducing the size in the horizontal direction (axial direction). For example, it is required to reduce the size of the power transmission device applicable to the 2-axis type and the 1-axis type in the axial direction.
  • the present invention has a hollow shaft and A differential gear connected to the downstream of the hollow shaft via a reduction gear, With a drive shaft connected downstream of the differential gear, The drive shaft is arranged so as to penetrate the hollow shaft.
  • the differential case of the differential gear has a support portion for supporting the drive shaft.
  • the support portion of the differential case is a power transmission device having a configuration inserted in the inner circumference of the hollow shaft.
  • the size can be reduced in the lateral direction (axial direction).
  • FIG. 1 is a diagram illustrating a power transmission device 1 according to an embodiment.
  • FIG. 2 is an enlarged view around the planetary reduction gear 5 of the power transmission device 1.
  • FIG. 3 is an enlarged view of the power transmission device 1 around the differential device 6.
  • the power transmission device 1 includes a motor 2, a planetary reduction gear 5 (reduction mechanism) that decelerates the output rotation of the motor 2 and inputs it to the differential device 6, and a drive shaft 8 (8A, 8B). There is.
  • a planetary reduction gear 5, a differential device 6, and drive shafts 8 (8A, 8B) are provided along the transmission path of the output rotation of the motor 2.
  • the output rotation of the motor 2 is decelerated by the planetary reduction gear 5 and input to the differential device 6, and then the left and right drive of the vehicle on which the power transmission device 1 is mounted via the drive shafts 8 (8A, 8B). It is transmitted to the ring (not shown).
  • the drive shaft 8A is rotatably connected to the left wheel of the vehicle equipped with the power transmission device 1
  • the drive shaft 8B is rotatably connected to the right wheel.
  • the planetary reduction gear 5 is connected downstream of the motor 2
  • the differential device 6 is connected downstream of the planetary reduction gear 5
  • the drive shafts 8 (8A, 8B) are differential devices. It is connected to the downstream of 6.
  • the motor 2 has a cylindrical motor shaft 20, a cylindrical rotor core 21 extrapolated to the motor shaft 20, and a stator core 25 that surrounds the outer circumference of the rotor core 21 at predetermined intervals.
  • the motor shaft 20 is extrapolated to the drive shaft 8B. In this state, the motor shaft 20 is rotatable relative to the drive shaft 8B. In the motor shaft 20, bearings B1 and B1 are extrapolated and fixed to the outer periphery on one end 20a side and the other end 20b side in the longitudinal direction.
  • One end 20a side of the motor shaft 20 is rotatably supported by a cylindrical motor support portion 121 of the intermediate cover 12 via a bearing B1.
  • the other end 20b side of the motor shaft 20 is rotatably supported by a cylindrical motor support portion 111 fixed to the cover 11 via a bearing B1.
  • the motor 2 has a motor housing 10 that surrounds the outer circumference of the rotor core 21 at predetermined intervals.
  • the intermediate cover 12 is joined to one end 10a of the motor housing 10, and the cover 11 is joined to the other end 10b of the motor housing 10.
  • Seal rings S and S are provided on one end 10a and the other end 10b of the motor housing 10.
  • One end 10a of the motor housing 10 is joined to the annular base 120 of the intermediate cover 12 without a gap by a seal ring S provided at the one end 10a.
  • the other end 10b of the motor housing 10 is joined to the annular joint 110 of the cover 11 without a gap by the seal ring S provided on the other end 10b.
  • the base portion 120 and the motor support portion 121 are provided so as to be displaced from each other in the rotation axis X direction.
  • the motor support portion 121 is inserted inside the motor housing 10.
  • the motor support portion 121 is arranged on the inner diameter side of the coil end 253a, which will be described later, with one end portion 21a of the rotor core 21 facing each other with a gap in the rotation axis X direction (see FIG. 2). Then, as shown in FIG. 2, the connecting portion 123 connecting the base portion 120 and the motor support portion 121 is provided on the inner diameter side of the coil end 253a in a direction along the rotation axis X.
  • a bearing retainer 125 is fixed to the end surface 121a of the motor support portion 121 on the rotor core 21 side.
  • the bearing retainer 125 has a ring shape when viewed from the rotation axis X direction.
  • the inner diameter side of the bearing retainer 125 is in contact with the side surface of the outer race B1b of the bearing B1 supported by the motor support portion 121 from the rotation axis X direction.
  • the bearing retainer 125 prevents the bearing B1 from falling off from the motor support portion 121.
  • the motor support portion 111 is located on the inner diameter side of the joint portion 110.
  • the motor support portion 111 is fixed to the side wall portion 113 of the cover 11 via a tubular wall portion 115 formed integrally with the motor support portion 111.
  • the motor support 111 when the joint 110 of the cover 11 is fixed to the other end 10b of the motor housing 10, the motor support 111 is attached to the other end 21b of the rotor core 21 on the inner diameter side of the coil end 253b described later. They are arranged so as to face each other with a gap in the X direction. In this state, the cylinder wall portion 115 extending from the motor support portion 111 is located on the inner diameter side of the coil end 253b.
  • the rotor core 21 is arranged between the motor support portion 111 on the cover 11 side and the motor support portion 121 on the intermediate cover 12 side.
  • the rotor core 21 is formed by laminating a plurality of silicon steel plates, and each of the silicon steel plates is extrapolated to the motor shaft 20 in a state where the relative rotation with the motor shaft 20 is restricted.
  • the silicon steel plate When viewed from the rotation axis X direction of the motor shaft 20, the silicon steel plate has a ring shape, and on the outer peripheral side of the silicon steel plate, magnets of N pole and S pole (not shown) alternate in the circumferential direction around the rotation axis X. It is provided in.
  • One end 21a of the rotor core 21 in the X direction of the rotation axis is positioned by the large diameter portion 203 of the motor shaft 20.
  • the other end 21b of the rotor core 21 is positioned by a stopper 23 press-fitted into the motor shaft 20.
  • the stator core 25 is formed by laminating a plurality of electromagnetic steel plates, and each of the electromagnetic steel plates has a ring-shaped yoke portion 251 fixed to the inner circumference of the motor housing 10 and a rotor core from the inner circumference of the yoke portion 251. It has a teeth portion 252 that protrudes to the 21 side.
  • a stator core 25 having a configuration in which the winding 253 is distributed and wound across a plurality of tooth portions 252 is adopted, and the stator core 25 is a coil end 253a, 253b protruding in the rotation axis X direction.
  • the length in the rotation axis X direction is longer than that of the rotor core 21 by the amount.
  • stator core is not limited to a distributed winding configuration.
  • a stator core having a configuration in which windings are centrally wound may be adopted for each of the plurality of tooth portions 252 protruding toward the rotor core 21 side.
  • the bearing B1 is press-fitted onto the outer periphery of a region 20a at one end of the large diameter portion 203.
  • the inner race B1a of the bearing B1 one side surface in the rotation axis X direction is in contact with the step portion 204 provided on the outer periphery of the motor shaft 20.
  • the inner race B1a has a ring-shaped stopper 205 press-fitted onto the outer periphery of the motor shaft 20 in contact with the other side surface.
  • the bearing B1 is positioned by the stopper 205 at a position where the inner race B1a is in contact with the step portion 204.
  • One end 20a of the motor shaft 20 is located on the planetary reduction gear 5 side (left side in the figure) with respect to the stopper 205.
  • One end 20a faces the meshing portion between the sun gear 51 of the planetary reduction gear 5 and the large-diameter gear portion 531 of the stepped pinion gear 53 at intervals in the X direction of the rotation axis.
  • the cylindrical wall 122 is located on the radial outside of the motor shaft 20.
  • the cylindrical wall 122 projects from the motor support portion 121 toward the planetary reduction gear 5 (left side in the drawing).
  • the cylindrical wall 122 surrounds the outer circumference of the motor shaft 20 at predetermined intervals, and a lip seal RS is installed between the cylindrical wall 122 and the motor shaft 20.
  • the lip seal RS is provided to partition the space Sa on the inner diameter side of the motor housing 10 and the space Sb on the inner diameter side of the case 13.
  • Lubricating oil OL is sealed in the space Sb on the inner diameter side of the case 13.
  • the lip seal RS is provided to prevent the lubricating oil OL from flowing into the space Sa on the inner diameter side of the motor housing 10.
  • a recess 124 opened on the planetary reduction gear 5 side (left side in FIG. 2) is formed between the cylindrical wall 122 and the connection portion 123.
  • a step portion 123a for positioning the outer race B3b of the bearing B3 is provided on the connecting portion 123 side (outer diameter side) of the recess 124.
  • the inner race B3a of the bearing B3 is provided so as to avoid contact with the motor support portion 121, and the inner race B3a supports the outer circumference of the tubular portion 552 described later.
  • the motor housing 10, the cover 11, the intermediate cover 12, and the case 13 constitute the main body case 9 of the power transmission device 1.
  • the internal space of the main body case 9 is defined by the intermediate cover 12, and the space Sa on the motor housing 10 side serves as a motor chamber for accommodating the motor 2.
  • the space Sb on the case 13 side serves as a gear chamber for accommodating the planetary reduction gear 5 and the differential device 6.
  • the connecting portion 202 on the one end 20a side of the motor shaft 20 is formed with an inner diameter larger than the region 201 in which the rotor core 21 is extrapolated.
  • a cylindrical connecting portion 511 of the sun gear 51 is inserted inside the connecting portion 202. In this state, the connecting portion 202 on the one end 20a side of the motor shaft 20 and the connecting portion 511 of the sun gear 51 are spline-fitted so as not to rotate relative to each other.
  • the output rotation of the motor 2 is input to the sun gear 51 of the planetary reduction gear 5 via the motor shaft 20, and the sun gear 51 rotates around the rotation axis X by the rotational driving force of the motor 2.
  • the connecting portion 202 of the motor shaft 20 and the connecting portion 511 on the planetary reduction gear 5 side are connected on the inner diameter side of the coil end 253a of the motor 2.
  • the sun gear 51 has a connecting portion 511 extending in the rotation axis X direction from the side surface 51a on the inner diameter side.
  • the connecting portion 511 is integrally formed with the sun gear 51, and a through hole 510 is formed so as to straddle the inner diameter side of the sun gear 51 and the inner diameter side of the connecting portion 511.
  • the sun gear 51 and the connecting portion 511 constitute the hollow shaft 50 according to the invention.
  • the hollow shaft 50 is extrapolated to the drive shaft 8B. In this state, the hollow shaft 50 (sun gear 51) is rotatable relative to the drive shaft 8B.
  • the sun gear 51 meshes with the large-diameter gear portion 531 of the stepped pinion gear 53 on the extension of the motor shaft 20 described above.
  • the stepped pinion gear 53 has a large-diameter gear portion 531 that meshes with the sun gear 51, and a small-diameter gear portion 532 that has a smaller diameter than the large-diameter gear portion 531.
  • the stepped pinion gear 53 is a gear component in which a large-diameter gear portion 531 and a small-diameter gear portion 532 are integrally provided side by side in the direction of the axis X1 parallel to the rotation axis X.
  • the stepped pinion gear 53 has a through hole 530 penetrating the inner diameter side of the large-diameter gear portion 531 and the small-diameter gear portion 532 in the axis X1 direction.
  • the stepped pinion gear 53 is rotatably supported on the outer circumference of the pinion shaft 54 penetrating the through hole 530 via the needle bearing NB.
  • needle bearings NB are provided on the inner diameter side of the large diameter gear portion 531 and on the inner diameter side of the small diameter gear portion 532, respectively.
  • the needle bearings NB and NB are arranged in series in the axis X1 direction on the outer circumference of the pinion shaft 54.
  • One end and the other end of the pinion shaft 54 in the longitudinal direction are supported by a side plate portion 651 formed integrally with the differential case 60 and a side plate portion 551 arranged at intervals from the side plate portion 651.
  • the side plate portions 651 and 551 are plate-shaped members provided in a direction orthogonal to the rotation axis X.
  • the side plate portions 651 and 551 are provided in parallel with each other at intervals in the rotation axis X direction.
  • a plurality (for example, three) of a plurality of stepped pinion gears 53 are provided between the side plate portions 651 and 551 at predetermined intervals in the circumferential direction around the rotation axis X.
  • Each of the small diameter gear portions 532 meshes with the inner circumference of the ring gear 52.
  • the ring gear 52 is spline-fitted on the inner circumference of the case 13, and the ring gear 52 is restricted from rotating relative to the case 13.
  • a tubular portion 552 extending toward the motor 2 side is provided.
  • the tubular portion 552 is inserted into the recess 124 of the intermediate cover 12 from the rotation axis X direction. In the recess 124, the tubular portion 552 is provided so as to avoid contact with the motor support portion 121.
  • the tubular portion 552 is located on the radial outer side of the meshing portion between the connecting portion 202 of the motor shaft 20 and the connecting portion 511 on the planetary reduction gear 5 side.
  • a bearing B3 having an outer race B3b fixed to a recess 124 is in contact with the outer periphery of the tubular portion 552.
  • the tubular portion 552 of the side plate portion 551 is rotatably supported by the intermediate cover 12 via the bearing B3.
  • one side plate portion 651 of the side plate portion 551 and the side plate portion 651 constituting the carrier 55 is integrally formed with the differential case 60 of the differential device 6. Therefore, the carrier 55 (side plate portions 551, 651, pinion shaft 54) of the planetary reduction gear 5 is formed substantially integrally with the differential case 60.
  • the output rotation of the motor 2 is input to the sun gear 51.
  • the output rotation input to the sun gear 51 is input to the stepped pinion gear 53 via the large-diameter gear portion 531 that meshes with the sun gear 51, and the stepped pinion gear 53 rotates around the axis X1.
  • the small-diameter gear portion 532 integrally formed with the large-diameter gear portion 531 rotates around the axis X1 integrally with the large-diameter gear portion 531.
  • the small-diameter gear portion 532 meshes with the ring gear 52 fixed to the inner circumference of the case 13. Therefore, when the small-diameter gear portion 532 rotates around the axis X1, the stepped pinion gear 53 rotates around the axis X1 while rotating around the axis X1.
  • the differential case 60 is interlocked with the displacement of the stepped pinion gear 53 around the rotation axis X in the circumferential direction. It rotates around the rotation axis X.
  • the outer diameter R2 of the small diameter gear portion 532 is smaller than the outer diameter R1 of the large diameter gear portion 531 (see FIG. 3).
  • the sun gear 51 is an input unit for the output rotation of the motor 2
  • the carrier 55 that supports the stepped pinion gear 53 is an output unit for the input rotation. Then, the rotation input to the sun gear 51 of the planetary reduction gear 5 is greatly decelerated by the stepped pinion gear 53, and then output to the differential case 60 in which the side plate portion 651 of the carrier 55 is integrally formed.
  • the differential case 60 is formed in a hollow shape in which the shaft 61, the bevel gears 62A and 62B, and the side gears 63A and 63B are housed therein.
  • tubular support portions 601 and 602 are provided on both sides of the rotation axis X direction (left-right direction in the drawing). The support portions 601 and 602 extend along the rotation axis X in a direction away from the shaft 61.
  • connection piece 56 for connecting the side plate portion 651 and the side plate portion 551 of the carrier 55 is provided on the outer diameter side of the support portion 601.
  • One end of the connection piece 56 on the differential case 60 side is provided so as to straddle the side plate portion 651 and the outer circumference of the differential case 60, and the other end is connected to the side plate portion 551 from the rotation axis X direction.
  • connection piece 56 is provided at a position avoiding interference with the stepped pinion gear 53 described above. As described above, a plurality (for example, three) of the stepped pinion gears 53 are provided at predetermined intervals in the circumferential direction around the rotation axis X. The connecting piece 56 is provided between the stepped pinion gears 53 adjacent to each other in the circumferential direction around the rotation axis X.
  • the inner race B2a of the bearing B2 is press-fitted onto the outer periphery of the support portion 602 of the differential case 60.
  • the outer race B2b of the bearing B2 is held by the ring-shaped support portion 131 of the case 13, and the support portion 602 of the differential case 60 is rotatably supported by the case 13 via the bearing B2.
  • a drive shaft 8A penetrating the opening 130 of the case 13 is inserted into the support portion 602 from the rotation axis X direction, and the drive shaft 8A is rotatably supported by the support portion 602.
  • a lip seal RS is fixed to the inner circumference of the opening 130, and the lip portion (not shown) of the lip seal RS elastically contacts the outer circumference of the drive shaft 8A to open the outer circumference of the drive shaft 8A.
  • the gap between the inner circumference and the inner circumference of the portion 130 is sealed.
  • the outer diameter R3 of the support portion 601 is formed to have an outer diameter smaller than the inner diameter R4 of the hollow shaft 50 (sun gear 51).
  • the support portion 601 is inserted inside the hollow shaft 50 from the rotation axis X direction, and in a region where the support portion 601 and the hollow shaft 50 (sun gear 51) overlap when viewed from the radial direction of the rotation shaft X, the support portion 601 is a support portion.
  • a needle bearing NB is provided between the outer circumference of 601 and the inner circumference of the hollow shaft 50.
  • the sun gear 51 side of the hollow shaft 50 is rotatably supported by the support portion 601 of the differential case 60 via the needle bearing NB.
  • the end portion 50a of the hollow shaft 50 on the differential case 60 side faces the side edge portion 60c of the differential case 60 with a gap in the rotation axis X direction.
  • a drive shaft 8B penetrating the opening 114 of the cover 11 is inserted into the support portion 601 of the differential case 60 from the rotation axis X direction.
  • the drive shaft 8B is provided so as to cross the inner diameter side of the motor shaft 20 of the motor 2 and the inner diameter side of the hollow shaft 50 in the rotation axis X direction, and the tip end side of the drive shaft 8B is rotatably supported by the support portion 601. Has been done.
  • a lip seal RS is fixed to the inner circumference of the opening 114 of the cover 11, and the lip portion (not shown) of the lip seal RS elastically contacts the outer circumference of the drive shaft 8B, so that the drive shaft 8B has a lip seal RS.
  • the gap between the outer circumference and the inner circumference of the opening 114 is sealed.
  • side gears 63A and 63B are spline-fitted on the outer periphery of the tip portions of the drive shafts 8A and 8B, and the side gears 63A and 63B and the drive shaft 8 (8A and 8B) are fitted.
  • the differential case 60 is provided with shaft holes 60a and 60b penetrating in a direction orthogonal to the rotation axis X at positions symmetrical with respect to the rotation axis X.
  • the shaft holes 60a and 60b are located on the axis Y orthogonal to the rotation axis X, and one end 61a side and the other end 61b side of the shaft 61 are inserted.
  • One end 61a side and the other end 61b side of the shaft 61 are fixed to the differential case 60 by a pin P, and the shaft 61 is prohibited from rotating around the axis Y.
  • the shaft 61 is located between the side gears 63A and 63B in the differential case 60, and is arranged along the axis Y.
  • bevel gears 62A and 62B are externally inserted and rotatably supported on the shaft 61.
  • Two bevel gears 62A and 62B are provided at intervals in the longitudinal direction of the shaft 61 (the axial direction of the axis Y), and the bevel gears 62A and 62B are arranged so that their teeth face each other. ing.
  • the bevel gears 62A and 62B are provided so that the axes of the bevel gears 62A and 62B are aligned with the axes of the shaft 61.
  • side gears 63A and 63B are located on both sides of the bevel gears 62A and 62B in the rotation axis X direction.
  • Two side gears 63A and 63B are provided with their teeth facing each other at intervals in the X direction of the rotation axis, and the bevel gears 62A and 62B and the side gears 63A and 63B have teeth of each other. Is assembled in a meshed state.
  • the lower side of the differential case 60 is immersed in the lubricating oil inside the case 13.
  • the lubricating oil is contained in the case 13 until the height at which one end 61a or the other end 61b of the shaft 61 is located at least in the lubricating oil. Is stored.
  • a planetary reduction gear 5 In the power transmission device 1, a planetary reduction gear 5, a differential device 6, and drive shafts 8 (8A, 8B) are provided along the transmission path of the output rotation of the motor 2.
  • the sun gear 51 is an input unit for the output rotation of the planetary reduction gear 5
  • the carrier 55 that supports the stepped pinion gear 53 is an output unit for the input rotation.
  • the stepped pinion gear 53 (large diameter gear portion 531 and small diameter gear portion 532) rotates around the axis X1 by the rotation input from the sun gear 51 side.
  • the small-diameter gear portion 532 of the stepped pinion gear 53 meshes with the ring gear 52 fixed to the inner circumference of the case 13. Therefore, the stepped pinion gear 53 rotates around the rotation axis X while rotating around the axis X1.
  • the outer diameter R2 of the small diameter gear portion 532 is smaller than the outer diameter R1 of the large diameter gear portion 531 (see FIG. 3).
  • the carriers 55 (side plate portions 551 and 651) that support the stepped pinion gear 53 rotate around the rotation axis X at a rotation speed lower than the rotation input from the motor 2 side. Therefore, the rotation input to the sun gear 51 of the planetary reduction gear 5 is greatly reduced by the stepped pinion gear 53, and then the side plate portion 651 of the carrier 55 is integrally formed with the differential case 60 (differential device 6). Is output to.
  • the support portion 601 of the differential case 60 is formed with an outer diameter R3 smaller than the inner diameter R4 of the hollow shaft 50, and the support portion 601 of the differential case 60 is formed on the inner circumference of the hollow shaft 50. It has been inserted. Therefore, when viewed from the radial direction of the rotating shaft X, a part of the hollow shaft 50 on the sun gear 51 side and the support portion 601 of the differential case 60 are arranged so as to overlap each other. As a result, the length of the power transmission device 1 in the rotation axis X direction (axis length direction) can be shortened by the length Lx at which the hollow shaft 50 and the support portion 601 of the differential case 60 overlap in the rotation axis X direction.
  • the rotation shaft X of the support portion 601 is used in order to shorten the length of the power transmission device 1 in the rotation shaft X direction. It is necessary to shorten the length in the direction.
  • the support portion 601 of the differential case 60 is inserted into the inner circumference of the hollow shaft 50 and arranged to support the drive shaft 8B while suppressing the length of the power transmission device 1 in the rotation axis X direction.
  • the length of the part 601 is secured.
  • the inner circumference of the support portion 601 of the differential case 60 rotatably supports the drive shaft 8B inserted in the support portion 601 and the outer circumference of the support portion 601 is the hollow shaft 50 via the needle bearing NB. It is rotatably supported on the inner circumference of the sun gear 51 side. Therefore, the length of the power transmission device 1 in the rotation axis X direction is suppressed while ensuring the support stability of the drive shaft 8B.
  • the power transmission device 1 has the following configuration.
  • the power transmission device 1 is Hollow shaft 50 and A differential device 6 (differential gear) connected to the downstream of the hollow shaft 50 via a planetary reduction gear 5 (reduction gear), Drive shafts 8 (8A, 8B) connected downstream of the differential device 6 and Have.
  • the drive shaft 8B is arranged so as to penetrate the hollow shaft 50.
  • the differential case 60 (differential case) of the differential device 6 has a support portion 601 that supports the drive shaft 8B.
  • the support portion 601 of the differential case 60 is inserted into the inner circumference of the hollow shaft 50.
  • the lengths of the support portions 601 and 602 in the rotation axis X direction are longer than a predetermined length for the support stability of the drive shaft 8 (8A, 8B). Is preferable.
  • the diameters of the hollow shaft 50 and the support portion 601 are substantially the same, the hollow shaft 50 and the support portion 601 interfere with each other, which hinders the shortening of the power transmission device 1 in the axial length direction (rotation axis X direction). It becomes. Therefore, the outer diameter of the support portion 601 is set to the outer diameter R3 that can be inserted into the hollow shaft 50.
  • the support stability of the drive shaft 8B at the support portion 601 can be ensured, and the differential case 60 can be arranged closer to the hollow shaft 50 side, so that the power transmission device 1 can be shortened in the axial length direction. It will be possible.
  • the power transmission device 1 has the following configuration. (2) The support portion 601 is supported on the inner circumference of the hollow shaft 50 via a needle bearing NB (bearing).
  • the needle bearing NB (bearing) on the inner peripheral side of the hollow shaft 50
  • the hollow shaft 50 and the support portion 601 of the differential case 60 can be provided so as to overlap each other when viewed from the radial direction of the rotating shaft X.
  • the differential case 60 and the hollow shaft 50 from interfering with each other in the radial direction.
  • the case where the support portion 601 is supported on the inner circumference of the hollow shaft 50 via the needle bearing NB (bearing) is illustrated.
  • an annular bush may be provided so that the support portion 601 is supported on the inner circumference of the hollow shaft 50 via the bush.
  • the bush is, for example, a metal ring that allows relative rotation between the hollow shaft and the support portion.
  • the axial direction can be shortened. In other words, by providing a clearance between the hollow shaft 50 and the differential case 60 in the axial direction, the axial direction can be shortened.
  • the power transmission device 1 has the following configuration. (3) In the transmission path of the output rotation of the motor 2 in the power transmission device 1, the motor 2 is connected upstream of the hollow shaft 50.
  • the drive shaft 8B is arranged so as to penetrate the inner circumference of the motor 2.
  • FIG. 4 is an enlarged view of the power transmission device 1A around the differential device 6 according to the modified example.
  • the case where the end portion 50a of the hollow shaft 50 on the differential case 60 side faces the side edge portion 60c of the differential case 60 with a gap in the rotation axis X direction is exemplified (see FIG. 3).
  • a needle bearing NB thrust bearing
  • FIG. 4 a needle bearing NB (thrust bearing) may be provided between the end portion 50a of the hollow shaft 50 on the differential case 60 side and the side edge portion 60c of the differential case 60.
  • downstream connection in the present specification means that there is a connection relationship in which power is transmitted from a component arranged upstream to a component arranged downstream.
  • the case of the planetary reduction gear 5 connected downstream of the motor 2 means that power is transmitted from the motor 2 to the planetary reduction gear 5.
  • direct connection in the present specification means that the members are connected so as to be able to transmit power without the intervention of other members such as a reduction mechanism, a speed increase mechanism, and a transmission mechanism whose reduction ratio is converted. Means.
  • the planetary reduction gear 5 adopting the stepped pinion gear 53 is illustrated, but the planetary reduction gear adopting the non-stepped pinion gear may be adopted.
  • connection mode between the output unit (motor shaft 20) of the motor 2 and the input unit (sun gear 51) of the planetary reduction gear 5 is not limited to that of the above-described embodiment.
  • the output unit (motor shaft 20) of the motor 2 and the input unit (sun gear 51) of the planetary reduction gear 5 may be connected to each other so that rotation can be transmitted via another gear component or the like.
  • the reduction mechanism is a planetary reduction gear 5 including a stepped pinion gear 53 and one planetary reduction gear 5 is provided on the transmission path of the output rotation of the motor 2 is illustrated. ..
  • the present invention is not limited to this aspect.
  • a plurality of planetary reduction gears may be arranged in series on the transmission path of the output rotation of the motor 2.

Abstract

A power transmission device (1) according to the present invention has: a hollow shaft (50); a differential device (6) connected via a planetary reduction gear (5) downstream from the hollow shaft (50); and drive shafts (8A), (8B) connected downstream from the differential device (6). The drive shaft (8B) is arranged so as to pass through the hollow shaft (50). A differential case (60) of the differential device (6) has a support section (601) supporting the drive shaft (8b). The support section (601) of the differential case (60) is inserted into the inner circumference of the hollow shaft (50).

Description

動力伝達装置Power transmission device
　本発明は、動力伝達装置に関する。 The present invention relates to a power transmission device.
　特許文献１から特許文献３には、動力伝達装置が開示されている。 Patent Documents 1 to 3 disclose a power transmission device.
　特許文献１の動力伝達装置は、回転伝達に関与する３つの回転軸が並列に並んでおり、縦方向（重力方向）にサイズアップしやすい（以下、３軸タイプと呼ぶこととする）。 In the power transmission device of Patent Document 1, three rotation axes involved in rotation transmission are arranged in parallel, and it is easy to increase the size in the vertical direction (gravity direction) (hereinafter, referred to as a three-axis type).
　特許文献２の動力伝達装置は、モータのロータが中空軸となっており、この中空軸の内部をドライブシャフトが貫通している。そのため、３軸タイプと比較して縦方向のサイズダウンが可能となるが、大きなカウンタギアを配置しているため、縦方向にサイズアップしてしまう（以下、２軸タイプと呼ぶこととする）。 In the power transmission device of Patent Document 2, the rotor of the motor is a hollow shaft, and the drive shaft penetrates the inside of the hollow shaft. Therefore, it is possible to reduce the size in the vertical direction compared to the 3-axis type, but because a large counter gear is arranged, the size is increased in the vertical direction (hereinafter referred to as the 2-axis type). ..
　特許文献３の動力伝達装置は、カウンタギアではなく、段付きピニオンを有する遊星減速ギアを用いており、２軸タイプと比較して縦方向のサイズダウンが可能となる（以下、１軸タイプと呼ぶこととする）。 The power transmission device of Patent Document 3 uses a planetary reduction gear having a stepped pinion instead of a counter gear, and can be downsized in the vertical direction as compared with the 2-axis type (hereinafter referred to as the 1-axis type). I will call it).
　２軸タイプおよび１軸タイプの動力伝達装置では、縦方向（重力方向）のサイズダウンが可能であるが、横方向（軸方向）のサイズダウンには課題がある。
　例えば、２軸タイプおよび１軸タイプなどに適用可能な動力伝達装置を、軸方向にサイズダウンすることが求められている。 The two-axis type and one-axis type power transmission devices can be reduced in size in the vertical direction (gravity direction), but there is a problem in reducing the size in the horizontal direction (axial direction).
For example, it is required to reduce the size of the power transmission device applicable to the 2-axis type and the 1-axis type in the axial direction.
特開２０１３－２２１５６６号公報Japanese Unexamined Patent Publication No. 2013-221566 特開２０１６－０８９８６０号公報Japanese Unexamined Patent Publication No. 2016-089860 特開２０１８－１０３６７６号公報Japanese Unexamined Patent Publication No. 2018-103676
　本発明は　中空軸と、
　前記中空軸の下流に減速ギアを介して接続されたデファレンシャルギアと、
　前記デファレンシャルギアの下流に接続されたドライブシャフトと、を有し、
　前記ドライブシャフトは、前記中空軸を貫通して配置されており、
　前記デファレンシャルギアのデファレンシャルケースは前記ドライブシャフトを支持する支持部を有し、
　前記デファレンシャルケースの前記支持部は、前記中空軸の内周に挿入されている構成の動力伝達装置とした。 The present invention has a hollow shaft and
A differential gear connected to the downstream of the hollow shaft via a reduction gear,
With a drive shaft connected downstream of the differential gear,
The drive shaft is arranged so as to penetrate the hollow shaft.
The differential case of the differential gear has a support portion for supporting the drive shaft.
The support portion of the differential case is a power transmission device having a configuration inserted in the inner circumference of the hollow shaft.
　本発明によれば、横方向（軸方向）にサイズダウンできる。 According to the present invention, the size can be reduced in the lateral direction (axial direction).
本実施形態にかかる動力伝達装置を説明する図である。It is a figure explaining the power transmission device which concerns on this embodiment. 動力伝達装置の減速機構周りの拡大図である。It is an enlarged view around the reduction mechanism of a power transmission device. 動力伝達装置の差動装置周りの拡大図である。It is an enlarged view around the differential device of a power transmission device. 変形例にかかる動力伝達装置の差動装置周りの拡大図である。It is an enlarged view around the differential device of the power transmission device which concerns on the modification.
　以下、本発明の実施形態を説明する。
　図１は、実施形態にかかる動力伝達装置１を説明する図である。
　図２は、動力伝達装置１の遊星減速ギア５周りの拡大図である。
　図３は、動力伝達装置１の差動装置６周りの拡大図である。 Hereinafter, embodiments of the present invention will be described.
FIG. 1 is a diagram illustrating a power transmission device 1 according to an embodiment.
FIG. 2 is an enlarged view around the planetary reduction gear 5 of the power transmission device 1.
FIG. 3 is an enlarged view of the power transmission device 1 around the differential device 6.
　動力伝達装置１は、モータ２と、モータ２の出力回転を減速して差動装置６に入力する遊星減速ギア５（減速機構）と、ドライブシャフト８（８Ａ、８Ｂ）と、を有している。 The power transmission device 1 includes a motor 2, a planetary reduction gear 5 (reduction mechanism) that decelerates the output rotation of the motor 2 and inputs it to the differential device 6, and a drive shaft 8 (8A, 8B). There is.
　動力伝達装置１では、モータ２の出力回転の伝達経路に沿って、遊星減速ギア５と、差動装置６と、ドライブシャフト８（８Ａ、８Ｂ）と、が設けられている。
　モータ２の出力回転は、遊星減速ギア５で減速されて差動装置６に入力された後、ドライブシャフト８（８Ａ、８Ｂ）を介して、動力伝達装置１が搭載された車両の左右の駆動輪（図示せず）に伝達される。図１では、ドライブシャフト８Ａが、動力伝達装置１を搭載した車両の左輪に回転伝達可能に接続されていると共に、ドライブシャフト８Ｂが、右輪に回転伝達可能に接続されている。 In the power transmission device 1, a planetary reduction gear 5, a differential device 6, and drive shafts 8 (8A, 8B) are provided along the transmission path of the output rotation of the motor 2.
The output rotation of the motor 2 is decelerated by the planetary reduction gear 5 and input to the differential device 6, and then the left and right drive of the vehicle on which the power transmission device 1 is mounted via the drive shafts 8 (8A, 8B). It is transmitted to the ring (not shown). In FIG. 1, the drive shaft 8A is rotatably connected to the left wheel of the vehicle equipped with the power transmission device 1, and the drive shaft 8B is rotatably connected to the right wheel.
　ここで、遊星減速ギア５は、モータ２の下流に接続されており、差動装置６は、遊星減速ギア５の下流に接続されており、ドライブシャフト８（８Ａ、８Ｂ）は、差動装置６の下流に接続されている。 Here, the planetary reduction gear 5 is connected downstream of the motor 2, the differential device 6 is connected downstream of the planetary reduction gear 5, and the drive shafts 8 (8A, 8B) are differential devices. It is connected to the downstream of 6.
　モータ２は、円筒状のモータシャフト２０と、モータシャフト２０に外挿された円筒状のロータコア２１と、ロータコア２１の外周を所定間隔で囲むステータコア２５とを、有している。 The motor 2 has a cylindrical motor shaft 20, a cylindrical rotor core 21 extrapolated to the motor shaft 20, and a stator core 25 that surrounds the outer circumference of the rotor core 21 at predetermined intervals.
　モータシャフト２０は、ドライブシャフト８Ｂに外挿されている。この状態においてモータシャフト２０は、ドライブシャフト８Ｂに対して相対回転可能である。
　モータシャフト２０では、長手方向の一端２０ａ側と他端２０ｂ側の外周に、ベアリングＢ１、Ｂ１が外挿されて固定されている。 The motor shaft 20 is extrapolated to the drive shaft 8B. In this state, the motor shaft 20 is rotatable relative to the drive shaft 8B.
In the motor shaft 20, bearings B1 and B1 are extrapolated and fixed to the outer periphery on one end 20a side and the other end 20b side in the longitudinal direction.
　モータシャフト２０の一端２０ａ側は、ベアリングＢ１を介して、中間カバー１２の円筒状のモータ支持部１２１で回転可能に支持されている。
　モータシャフト２０の他端２０ｂ側は、ベアリングＢ１を介して、カバー１１に固定された円筒状のモータ支持部１１１で回転可能に支持されている。 One end 20a side of the motor shaft 20 is rotatably supported by a cylindrical motor support portion 121 of the intermediate cover 12 via a bearing B1.
The other end 20b side of the motor shaft 20 is rotatably supported by a cylindrical motor support portion 111 fixed to the cover 11 via a bearing B1.
　モータ２は、ロータコア２１の外周を所定間隔で囲むモータハウジング１０を有している。本実施形態では、モータハウジング１０の一端１０ａに、中間カバー１２が接合されており、モータハウジング１０の他端１０ｂに、カバー１１が接合されている。 The motor 2 has a motor housing 10 that surrounds the outer circumference of the rotor core 21 at predetermined intervals. In the present embodiment, the intermediate cover 12 is joined to one end 10a of the motor housing 10, and the cover 11 is joined to the other end 10b of the motor housing 10.
　モータハウジング１０の一端１０ａと他端１０ｂには、シールリングＳ、Ｓが設けられている。モータハウジング１０の一端１０ａは、当該一端１０ａに設けたシールリングＳにより、中間カバー１２の環状の基部１２０に隙間なく接合されている。
　モータハウジング１０の他端１０ｂは、当該他端１０ｂに設けたシールリングＳにより、カバー１１の環状の接合部１１０に隙間なく接合されている。 Seal rings S and S are provided on one end 10a and the other end 10b of the motor housing 10. One end 10a of the motor housing 10 is joined to the annular base 120 of the intermediate cover 12 without a gap by a seal ring S provided at the one end 10a.
The other end 10b of the motor housing 10 is joined to the annular joint 110 of the cover 11 without a gap by the seal ring S provided on the other end 10b.
　中間カバー１２では、基部１２０とモータ支持部１２１とが、回転軸Ｘ方向で位置をずらして設けられている。
　本実施形態では、中間カバー１２をモータハウジング１０の一端１０ａに固定すると、モータ支持部１２１が、モータハウジング１０の内側に挿入されるようになっている。 In the intermediate cover 12, the base portion 120 and the motor support portion 121 are provided so as to be displaced from each other in the rotation axis X direction.
In the present embodiment, when the intermediate cover 12 is fixed to one end 10a of the motor housing 10, the motor support portion 121 is inserted inside the motor housing 10.
　この状態においてモータ支持部１２１は、後記するコイルエンド２５３ａの内径側で、ロータコア２１の一端部２１ａに、回転軸Ｘ方向の隙間をあけて対向して配置される（図２参照）。
　そして、図２に示すように、基部１２０とモータ支持部１２１とを接続する接続部１２３は、コイルエンド２５３ａの内径側で、回転軸Ｘに沿う向きに設けられている。 In this state, the motor support portion 121 is arranged on the inner diameter side of the coil end 253a, which will be described later, with one end portion 21a of the rotor core 21 facing each other with a gap in the rotation axis X direction (see FIG. 2).
Then, as shown in FIG. 2, the connecting portion 123 connecting the base portion 120 and the motor support portion 121 is provided on the inner diameter side of the coil end 253a in a direction along the rotation axis X.
　モータ支持部１２１のロータコア２１側の端面１２１ａには、ベアリングリテーナ１２５が固定されている。
　ベアリングリテーナ１２５は、回転軸Ｘ方向から見てリング状を成している。ベアリングリテーナ１２５の内径側は、モータ支持部１２１で支持されたベアリングＢ１のアウタレースＢ１ｂの側面に回転軸Ｘ方向から当接している。ベアリングリテーナ１２５は、モータ支持部１２１からのベアリングＢ１の脱落を阻止している。 A bearing retainer 125 is fixed to the end surface 121a of the motor support portion 121 on the rotor core 21 side.
The bearing retainer 125 has a ring shape when viewed from the rotation axis X direction. The inner diameter side of the bearing retainer 125 is in contact with the side surface of the outer race B1b of the bearing B1 supported by the motor support portion 121 from the rotation axis X direction. The bearing retainer 125 prevents the bearing B1 from falling off from the motor support portion 121.
　図１に示すように、カバー１１では、接合部１１０の内径側にモータ支持部１１１が位置している。
　モータ支持部１１１は、当該モータ支持部１１１と一体に形成された筒壁部１１５を介して、カバー１１の側壁部１１３に固定されている。 As shown in FIG. 1, in the cover 11, the motor support portion 111 is located on the inner diameter side of the joint portion 110.
The motor support portion 111 is fixed to the side wall portion 113 of the cover 11 via a tubular wall portion 115 formed integrally with the motor support portion 111.
　本実施形態では、カバー１１の接合部１１０をモータハウジング１０の他端１０ｂに固定すると、モータ支持部１１１が、後記するコイルエンド２５３ｂの内径側で、ロータコア２１の他端部２１ｂに、回転軸Ｘ方向の隙間をあけて対向して配置される。
　この状態において、モータ支持部１１１から延びる筒壁部１１５は、コイルエンド２５３ｂの内径側に位置している。 In the present embodiment, when the joint 110 of the cover 11 is fixed to the other end 10b of the motor housing 10, the motor support 111 is attached to the other end 21b of the rotor core 21 on the inner diameter side of the coil end 253b described later. They are arranged so as to face each other with a gap in the X direction.
In this state, the cylinder wall portion 115 extending from the motor support portion 111 is located on the inner diameter side of the coil end 253b.
　図１に示すように、モータハウジング１０の内側では、カバー１１側のモータ支持部１１１と、中間カバー１２側のモータ支持部１２１との間に、ロータコア２１が配置されている。 As shown in FIG. 1, inside the motor housing 10, the rotor core 21 is arranged between the motor support portion 111 on the cover 11 side and the motor support portion 121 on the intermediate cover 12 side.
　ロータコア２１は、複数の珪素鋼板を積層して形成したものであり、珪素鋼板の各々は、モータシャフト２０との相対回転が規制された状態で、モータシャフト２０に外挿されている。
　モータシャフト２０の回転軸Ｘ方向から見て、珪素鋼板はリング状を成しており、珪素鋼板の外周側では、図示しないＮ極とＳ極の磁石が、回転軸Ｘ周りの周方向に交互に設けられている。 The rotor core 21 is formed by laminating a plurality of silicon steel plates, and each of the silicon steel plates is extrapolated to the motor shaft 20 in a state where the relative rotation with the motor shaft 20 is restricted.
When viewed from the rotation axis X direction of the motor shaft 20, the silicon steel plate has a ring shape, and on the outer peripheral side of the silicon steel plate, magnets of N pole and S pole (not shown) alternate in the circumferential direction around the rotation axis X. It is provided in.
　回転軸Ｘ方向におけるロータコア２１の一端部２１ａは、モータシャフト２０の大径部２０３で位置決めされている。ロータコア２１の他端部２１ｂは、モータシャフト２０に圧入されたストッパ２３で位置決めされている。 One end 21a of the rotor core 21 in the X direction of the rotation axis is positioned by the large diameter portion 203 of the motor shaft 20. The other end 21b of the rotor core 21 is positioned by a stopper 23 press-fitted into the motor shaft 20.
　ステータコア２５は、複数の電磁鋼板を積層して形成したものであり、電磁鋼板の各々は、モータハウジング１０の内周に固定されたリング状のヨーク部２５１と、ヨーク部２５１の内周からロータコア２１側に突出するティース部２５２を、有している。
　本実施形態では、巻線２５３を、複数のティース部２５２に跨がって分布巻きした構成のステータコア２５を採用しており、ステータコア２５は、回転軸Ｘ方向に突出するコイルエンド２５３ａ、２５３ｂの分だけ、ロータコア２１よりも回転軸Ｘ方向の長さが長くなっている。 The stator core 25 is formed by laminating a plurality of electromagnetic steel plates, and each of the electromagnetic steel plates has a ring-shaped yoke portion 251 fixed to the inner circumference of the motor housing 10 and a rotor core from the inner circumference of the yoke portion 251. It has a teeth portion 252 that protrudes to the 21 side.
In the present embodiment, a stator core 25 having a configuration in which the winding 253 is distributed and wound across a plurality of tooth portions 252 is adopted, and the stator core 25 is a coil end 253a, 253b protruding in the rotation axis X direction. The length in the rotation axis X direction is longer than that of the rotor core 21 by the amount.
　なお、ステータコアは、分布巻きした構成のみに限定されない。ロータコア２１側に突出する複数のティース部２５２の各々に、巻線を集中巻きした構成のステータコアを採用しても良い。 Note that the stator core is not limited to a distributed winding configuration. A stator core having a configuration in which windings are centrally wound may be adopted for each of the plurality of tooth portions 252 protruding toward the rotor core 21 side.
　モータシャフト２０では、大径部２０３よりも一端２０ａ側の領域の外周に、ベアリングＢ１が圧入されている。
　図２に示すように、ベアリングＢ１のインナレースＢ１ａは、回転軸Ｘ方向の一方の側面が、モータシャフト２０の外周に設けた段部２０４に当接している。インナレースＢ１ａは、他方の側面に、モータシャフト２０の外周に圧入されたリング状のストッパ２０５が当接している。
　ストッパ２０５によりベアリングＢ１は、インナレースＢ１ａを、段部２０４に当接させた位置で位置決めされている。 In the motor shaft 20, the bearing B1 is press-fitted onto the outer periphery of a region 20a at one end of the large diameter portion 203.
As shown in FIG. 2, in the inner race B1a of the bearing B1, one side surface in the rotation axis X direction is in contact with the step portion 204 provided on the outer periphery of the motor shaft 20. The inner race B1a has a ring-shaped stopper 205 press-fitted onto the outer periphery of the motor shaft 20 in contact with the other side surface.
The bearing B1 is positioned by the stopper 205 at a position where the inner race B1a is in contact with the step portion 204.
　モータシャフト２０の一端２０ａは、ストッパ２０５よりも遊星減速ギア５側（図中、左側）に位置している。回転軸Ｘ方向において一端２０ａは、遊星減速ギア５のサンギア５１と、段付きピニオンギア５３の大径歯車部５３１との噛み合い部分に、間隔をあけて対向している。 One end 20a of the motor shaft 20 is located on the planetary reduction gear 5 side (left side in the figure) with respect to the stopper 205. One end 20a faces the meshing portion between the sun gear 51 of the planetary reduction gear 5 and the large-diameter gear portion 531 of the stepped pinion gear 53 at intervals in the X direction of the rotation axis.
　モータシャフト２０の一端２０ａ側では、モータシャフト２０の径方向外側に、円筒壁１２２が位置している。円筒壁１２２は、モータ支持部１２１から遊星減速ギア５側（図中、左側）に突出している。 On one end 20a side of the motor shaft 20, the cylindrical wall 122 is located on the radial outside of the motor shaft 20. The cylindrical wall 122 projects from the motor support portion 121 toward the planetary reduction gear 5 (left side in the drawing).
　円筒壁１２２は、モータシャフト２０の外周を所定間隔で囲んでおり、円筒壁１２２とモータシャフト２０との間には、リップシールＲＳが設置されている。
　リップシールＲＳは、モータハウジング１０の内径側の空間Ｓａと、ケース１３の内径側の空間Ｓｂとを、区画するために設けられている。 The cylindrical wall 122 surrounds the outer circumference of the motor shaft 20 at predetermined intervals, and a lip seal RS is installed between the cylindrical wall 122 and the motor shaft 20.
The lip seal RS is provided to partition the space Sa on the inner diameter side of the motor housing 10 and the space Sb on the inner diameter side of the case 13.
　ケース１３の内径側の空間Ｓｂには、潤滑油ＯＬが封入されている。リップシールＲＳは、モータハウジング１０の内径側の空間Ｓａへの潤滑油ＯＬの流入を阻止するために設けられている。 Lubricating oil OL is sealed in the space Sb on the inner diameter side of the case 13. The lip seal RS is provided to prevent the lubricating oil OL from flowing into the space Sa on the inner diameter side of the motor housing 10.
　図２に示すように、円筒壁１２２の外径側では、前記した接続部１２３との間に、遊星減速ギア５側（図２における左側）に開口した凹部１２４が形成されている。
　凹部１２４の接続部１２３側（外径側）には、ベアリングＢ３のアウタレースＢ３ｂを位置決めする段部１２３ａが設けられている。凹部１２４内において、ベアリングＢ３のインナレースＢ３ａは、モータ支持部１２１との接触を避けて設けられており、インナレースＢ３ａは、後記する筒状部５５２の外周を支持している。 As shown in FIG. 2, on the outer diameter side of the cylindrical wall 122, a recess 124 opened on the planetary reduction gear 5 side (left side in FIG. 2) is formed between the cylindrical wall 122 and the connection portion 123.
A step portion 123a for positioning the outer race B3b of the bearing B3 is provided on the connecting portion 123 side (outer diameter side) of the recess 124. In the recess 124, the inner race B3a of the bearing B3 is provided so as to avoid contact with the motor support portion 121, and the inner race B3a supports the outer circumference of the tubular portion 552 described later.
　図１に示すように、本実施形態では、モータハウジング１０と、カバー１１と、中間カバー１２と、ケース１３とで、動力伝達装置１の本体ケース９を構成している。
　本体ケース９の内部空間は、中間カバー１２を境にして、モータハウジング１０側の空間Ｓａが、モータ２を収容するモータ室となっている。そして、ケース１３側の空間Ｓｂが、遊星減速ギア５と差動装置６を収容するギア室となっている。 As shown in FIG. 1, in the present embodiment, the motor housing 10, the cover 11, the intermediate cover 12, and the case 13 constitute the main body case 9 of the power transmission device 1.
The internal space of the main body case 9 is defined by the intermediate cover 12, and the space Sa on the motor housing 10 side serves as a motor chamber for accommodating the motor 2. The space Sb on the case 13 side serves as a gear chamber for accommodating the planetary reduction gear 5 and the differential device 6.
　図２に示すように、モータシャフト２０の一端２０ａ側の連結部２０２は、ロータコア２１が外挿された領域２０１よりも大きい内径で形成されている。
　連結部２０２の内側には、サンギア５１の円筒状の連結部５１１が挿入されている。この状態において、モータシャフト２０の一端２０ａ側の連結部２０２と、サンギア５１の連結部５１１とが、相対回転不能にスプライン嵌合している。 As shown in FIG. 2, the connecting portion 202 on the one end 20a side of the motor shaft 20 is formed with an inner diameter larger than the region 201 in which the rotor core 21 is extrapolated.
A cylindrical connecting portion 511 of the sun gear 51 is inserted inside the connecting portion 202. In this state, the connecting portion 202 on the one end 20a side of the motor shaft 20 and the connecting portion 511 of the sun gear 51 are spline-fitted so as not to rotate relative to each other.
　そのため、モータ２の出力回転が、モータシャフト２０を介して、遊星減速ギア５のサンギア５１に入力されて、サンギア５１がモータ２の回転駆動力で、回転軸Ｘ回りに回転する。
　本実施形態では、モータ２のコイルエンド２５３ａの内径側で、モータシャフト２０の連結部２０２と、遊星減速ギア５側の連結部５１１とが連結されている。 Therefore, the output rotation of the motor 2 is input to the sun gear 51 of the planetary reduction gear 5 via the motor shaft 20, and the sun gear 51 rotates around the rotation axis X by the rotational driving force of the motor 2.
In the present embodiment, the connecting portion 202 of the motor shaft 20 and the connecting portion 511 on the planetary reduction gear 5 side are connected on the inner diameter side of the coil end 253a of the motor 2.
　サンギア５１は、内径側の側面５１ａから回転軸Ｘ方向に延びる連結部５１１を有している。連結部５１１は、サンギア５１と一体に形成されおり、サンギア５１の内径側と連結部５１１の内径側とに跨がって、貫通孔５１０が形成されている。
　ここで、サンギア５１と連結部５１１とで、発明にかかる中空軸５０を構成している。 The sun gear 51 has a connecting portion 511 extending in the rotation axis X direction from the side surface 51a on the inner diameter side. The connecting portion 511 is integrally formed with the sun gear 51, and a through hole 510 is formed so as to straddle the inner diameter side of the sun gear 51 and the inner diameter side of the connecting portion 511.
Here, the sun gear 51 and the connecting portion 511 constitute the hollow shaft 50 according to the invention.
　中空軸５０は、ドライブシャフト８Ｂに外挿されている。この状態において、中空軸５０（サンギア５１）は、ドライブシャフト８Ｂに対して相対回転可能である。 The hollow shaft 50 is extrapolated to the drive shaft 8B. In this state, the hollow shaft 50 (sun gear 51) is rotatable relative to the drive shaft 8B.
　サンギア５１は、前記したモータシャフト２０の延長上で、段付きピニオンギア５３の大径歯車部５３１に噛合している。 The sun gear 51 meshes with the large-diameter gear portion 531 of the stepped pinion gear 53 on the extension of the motor shaft 20 described above.
　段付きピニオンギア５３は、サンギア５１に噛合する大径歯車部５３１と、大径歯車部５３１よりも小径の小径歯車部５３２とを有している。
　段付きピニオンギア５３は、大径歯車部５３１と小径歯車部５３２が、回転軸Ｘに平行な軸線Ｘ１方向で並んで、一体に設けられたギア部品である。 The stepped pinion gear 53 has a large-diameter gear portion 531 that meshes with the sun gear 51, and a small-diameter gear portion 532 that has a smaller diameter than the large-diameter gear portion 531.
The stepped pinion gear 53 is a gear component in which a large-diameter gear portion 531 and a small-diameter gear portion 532 are integrally provided side by side in the direction of the axis X1 parallel to the rotation axis X.
　段付きピニオンギア５３は、大径歯車部５３１と小径歯車部５３２の内径側を軸線Ｘ１方向に貫通した貫通孔５３０を有している。
　段付きピニオンギア５３は、貫通孔５３０を貫通したピニオン軸５４の外周で、ニードルベアリングＮＢを介して回転可能に支持されている。 The stepped pinion gear 53 has a through hole 530 penetrating the inner diameter side of the large-diameter gear portion 531 and the small-diameter gear portion 532 in the axis X1 direction.
The stepped pinion gear 53 is rotatably supported on the outer circumference of the pinion shaft 54 penetrating the through hole 530 via the needle bearing NB.
　ピニオン軸５４の外周では、大径歯車部５３１の内径側と、小径歯車部５３２の内径側に、ニードルベアリングＮＢがそれぞれ設けられている。ピニオン軸５４の外周においてニードルベアリングＮＢ、ＮＢは、軸線Ｘ１方向に直列に並んでいる。 On the outer circumference of the pinion shaft 54, needle bearings NB are provided on the inner diameter side of the large diameter gear portion 531 and on the inner diameter side of the small diameter gear portion 532, respectively. The needle bearings NB and NB are arranged in series in the axis X1 direction on the outer circumference of the pinion shaft 54.
　ピニオン軸５４の長手方向の一端と他端は、デフケース６０と一体に形成された側板部６５１と、この側板部６５１に間隔をあけて配置された側板部５５１で支持されている。
　側板部６５１、５５１は、回転軸Ｘに直交する向きで設けられた板状部材である。側板部６５１、５５１は、回転軸Ｘ方向に間隔をあけて互いに平行に設けられている。
　側板部６５１、５５１の間では、複数の段付きピニオンギア５３が、回転軸Ｘ周りの周方向に所定間隔で複数（例えば、３つ）設けられている。 One end and the other end of the pinion shaft 54 in the longitudinal direction are supported by a side plate portion 651 formed integrally with the differential case 60 and a side plate portion 551 arranged at intervals from the side plate portion 651.
The side plate portions 651 and 551 are plate-shaped members provided in a direction orthogonal to the rotation axis X. The side plate portions 651 and 551 are provided in parallel with each other at intervals in the rotation axis X direction.
A plurality (for example, three) of a plurality of stepped pinion gears 53 are provided between the side plate portions 651 and 551 at predetermined intervals in the circumferential direction around the rotation axis X.
　小径歯車部５３２の各々は、リングギア５２の内周に噛合している。リングギア５２は、ケース１３の内周にスプライン嵌合しており、リングギア５２は、ケース１３との相対回転が規制されている。 Each of the small diameter gear portions 532 meshes with the inner circumference of the ring gear 52. The ring gear 52 is spline-fitted on the inner circumference of the case 13, and the ring gear 52 is restricted from rotating relative to the case 13.
　ピニオン軸５４を支持する側板部５５１の内径側には、モータ２側に延びる筒状部５５２が設けられている。筒状部５５２は、中間カバー１２の凹部１２４に、回転軸Ｘ方向から挿入されている。凹部１２４内において、筒状部５５２は、モータ支持部１２１との接触を避けて設けられている。 On the inner diameter side of the side plate portion 551 that supports the pinion shaft 54, a tubular portion 552 extending toward the motor 2 side is provided. The tubular portion 552 is inserted into the recess 124 of the intermediate cover 12 from the rotation axis X direction. In the recess 124, the tubular portion 552 is provided so as to avoid contact with the motor support portion 121.
　筒状部５５２は、モータシャフト２０の連結部２０２と、遊星減速ギア５側の連結部５１１との噛み合い部分の径方向外側に位置している。筒状部５５２の外周には、凹部１２４にアウタレースＢ３ｂが固定されたベアリングＢ３が接触している。側板部５５１の筒状部５５２は、ベアリングＢ３を介して、中間カバー１２で回転可能に支持されている。 The tubular portion 552 is located on the radial outer side of the meshing portion between the connecting portion 202 of the motor shaft 20 and the connecting portion 511 on the planetary reduction gear 5 side. A bearing B3 having an outer race B3b fixed to a recess 124 is in contact with the outer periphery of the tubular portion 552. The tubular portion 552 of the side plate portion 551 is rotatably supported by the intermediate cover 12 via the bearing B3.
　遊星減速ギア５では、キャリア５５を構成する側板部５５１と側板部６５１のうちの一方の側板部６５１が、差動装置６のデフケース６０と一体に形成されている。
　そのため、遊星減速ギア５のキャリア５５（側板部５５１、６５１、ピニオン軸５４）は、デフケース６０と実質的に一体に形成されている。 In the planetary reduction gear 5, one side plate portion 651 of the side plate portion 551 and the side plate portion 651 constituting the carrier 55 is integrally formed with the differential case 60 of the differential device 6.
Therefore, the carrier 55 ( side plate portions 551, 651, pinion shaft 54) of the planetary reduction gear 5 is formed substantially integrally with the differential case 60.
　遊星減速ギア５では、モータ２の出力回転が、サンギア５１に入力される。
　サンギア５１に入力された出力回転は、サンギア５１に噛合する大径歯車部５３１を介して、段付きピニオンギア５３に入力されて、段付きピニオンギア５３が軸線Ｘ１回りに回転する。 In the planetary reduction gear 5, the output rotation of the motor 2 is input to the sun gear 51.
The output rotation input to the sun gear 51 is input to the stepped pinion gear 53 via the large-diameter gear portion 531 that meshes with the sun gear 51, and the stepped pinion gear 53 rotates around the axis X1.
　そうすると、大径歯車部５３１と一体に形成された小径歯車部５３２は、大径歯車部５３１と一体に軸線Ｘ１周りに回転する。
　ここで、小径歯車部５３２は、ケース１３の内周に固定されたリングギア５２に噛合している。そのため、小径歯車部５３２が軸線Ｘ１回りに回転すると、段付きピニオンギア５３は、軸線Ｘ１回りに自転しながら、回転軸Ｘ周りに回転する。 Then, the small-diameter gear portion 532 integrally formed with the large-diameter gear portion 531 rotates around the axis X1 integrally with the large-diameter gear portion 531.
Here, the small-diameter gear portion 532 meshes with the ring gear 52 fixed to the inner circumference of the case 13. Therefore, when the small-diameter gear portion 532 rotates around the axis X1, the stepped pinion gear 53 rotates around the axis X1 while rotating around the axis X1.
　そうすると、ピニオン軸５４の一端が、デフケース６０と一体に形成された側板部６５１に支持されているので、段付きピニオンギア５３の回転軸Ｘ周りの周方向の変位に連動して、デフケース６０が回転軸Ｘ回りに回転する。 Then, since one end of the pinion shaft 54 is supported by the side plate portion 651 formed integrally with the differential case 60, the differential case 60 is interlocked with the displacement of the stepped pinion gear 53 around the rotation axis X in the circumferential direction. It rotates around the rotation axis X.
　ここで、段付きピニオンギア５３では、小径歯車部５３２の外径Ｒ２が大径歯車部５３１の外径Ｒ１よりも小さくなっている（図３参照）。
　そして、遊星減速ギア５では、サンギア５１が、モータ２の出力回転の入力部となっており、段付きピニオンギア５３を支持するキャリア５５が、入力された回転の出力部となっている。
　そうすると、遊星減速ギア５のサンギア５１に入力された回転は、段付きピニオンギア５３により大きく減速されたのちに、キャリア５５の側板部６５１が一体に形成されたデフケース６０に出力される。 Here, in the stepped pinion gear 53, the outer diameter R2 of the small diameter gear portion 532 is smaller than the outer diameter R1 of the large diameter gear portion 531 (see FIG. 3).
In the planetary reduction gear 5, the sun gear 51 is an input unit for the output rotation of the motor 2, and the carrier 55 that supports the stepped pinion gear 53 is an output unit for the input rotation.
Then, the rotation input to the sun gear 51 of the planetary reduction gear 5 is greatly decelerated by the stepped pinion gear 53, and then output to the differential case 60 in which the side plate portion 651 of the carrier 55 is integrally formed.
　図３に示すように、デフケース６０は、シャフト６１と、かさ歯車６２Ａ、６２Ｂと、サイドギア６３Ａ、６３Ｂとを、内部に収納する中空状に形成されている。
　デフケース６０では、回転軸Ｘ方向（図中、左右方向）の両側部に、筒状の支持部６０１、６０２が設けられている。支持部６０１、６０２は、シャフト６１から離れる方向に、回転軸Ｘに沿って延出している。 As shown in FIG. 3, the differential case 60 is formed in a hollow shape in which the shaft 61, the bevel gears 62A and 62B, and the side gears 63A and 63B are housed therein.
In the differential case 60, tubular support portions 601 and 602 are provided on both sides of the rotation axis X direction (left-right direction in the drawing). The support portions 601 and 602 extend along the rotation axis X in a direction away from the shaft 61.
　支持部６０１の外径側には、キャリア５５の側板部６５１と側板部５５１とを接続する接続片５６が設けられている。
　接続片５６のデフケース６０側の一端は、側板部６５１とデフケース６０の外周とに跨がって設けられており、他端は、回転軸Ｘ方向から側板部５５１に接続されている。 On the outer diameter side of the support portion 601, a connection piece 56 for connecting the side plate portion 651 and the side plate portion 551 of the carrier 55 is provided.
One end of the connection piece 56 on the differential case 60 side is provided so as to straddle the side plate portion 651 and the outer circumference of the differential case 60, and the other end is connected to the side plate portion 551 from the rotation axis X direction.
　接続片５６は、前記した段付きピニオンギア５３との干渉を避けた位置に設けられている。前記したように、段付きピニオンギア５３は、回転軸Ｘ周りの周方向に所定間隔で複数（例えば、３つ）設けられている。
　接続片５６は、回転軸Ｘ回りの周方向で隣接する段付きピニオンギア５３の間に設けられている。 The connection piece 56 is provided at a position avoiding interference with the stepped pinion gear 53 described above. As described above, a plurality (for example, three) of the stepped pinion gears 53 are provided at predetermined intervals in the circumferential direction around the rotation axis X.
The connecting piece 56 is provided between the stepped pinion gears 53 adjacent to each other in the circumferential direction around the rotation axis X.
　デフケース６０の支持部６０２の外周には、ベアリングＢ２のインナレースＢ２ａが圧入されている。
　ベアリングＢ２のアウタレースＢ２ｂは、ケース１３のリング状の支持部１３１で保持されており、デフケース６０の支持部６０２は、ベアリングＢ２を介して、ケース１３で回転可能に支持されている。 The inner race B2a of the bearing B2 is press-fitted onto the outer periphery of the support portion 602 of the differential case 60.
The outer race B2b of the bearing B2 is held by the ring-shaped support portion 131 of the case 13, and the support portion 602 of the differential case 60 is rotatably supported by the case 13 via the bearing B2.
　支持部６０２には、ケース１３の開口部１３０を貫通したドライブシャフト８Ａが、回転軸Ｘ方向から挿入されており、ドライブシャフト８Ａは、支持部６０２で回転可能に支持されている。
　開口部１３０の内周には、リップシールＲＳが固定されており、リップシールＲＳの図示しないリップ部が、ドライブシャフト８Ａの外周に弾発的に接触することで、ドライブシャフト８Ａの外周と開口部１３０の内周との隙間が封止されている。 A drive shaft 8A penetrating the opening 130 of the case 13 is inserted into the support portion 602 from the rotation axis X direction, and the drive shaft 8A is rotatably supported by the support portion 602.
A lip seal RS is fixed to the inner circumference of the opening 130, and the lip portion (not shown) of the lip seal RS elastically contacts the outer circumference of the drive shaft 8A to open the outer circumference of the drive shaft 8A. The gap between the inner circumference and the inner circumference of the portion 130 is sealed.
　図３に示すように、本実施形態では、支持部６０１の外径Ｒ３は、中空軸５０（サンギア５１）の内径Ｒ４よりも小さい外径で形成されている。
　支持部６０１は、中空軸５０の内側に回転軸Ｘ方向から挿入されており、回転軸Ｘの径方向から見て、支持部６０１と中空軸５０（サンギア５１）とが重なる領域では、支持部６０１の外周と中空軸５０の内周との間に、ニードルベアリングＮＢが設けられている。
　中空軸５０のサンギア５１側は、デフケース６０の支持部６０１で、ニードルベアリングＮＢを介して回転可能に支持されている。 As shown in FIG. 3, in the present embodiment, the outer diameter R3 of the support portion 601 is formed to have an outer diameter smaller than the inner diameter R4 of the hollow shaft 50 (sun gear 51).
The support portion 601 is inserted inside the hollow shaft 50 from the rotation axis X direction, and in a region where the support portion 601 and the hollow shaft 50 (sun gear 51) overlap when viewed from the radial direction of the rotation shaft X, the support portion 601 is a support portion. A needle bearing NB is provided between the outer circumference of 601 and the inner circumference of the hollow shaft 50.
The sun gear 51 side of the hollow shaft 50 is rotatably supported by the support portion 601 of the differential case 60 via the needle bearing NB.
　中空軸５０のデフケース６０側の端部５０ａは、デフケース６０の側縁部６０ｃに、回転軸Ｘ方向の隙間をあけて対向している。 The end portion 50a of the hollow shaft 50 on the differential case 60 side faces the side edge portion 60c of the differential case 60 with a gap in the rotation axis X direction.
　図１に示すように、デフケース６０の支持部６０１には、カバー１１の開口部１１４を貫通したドライブシャフト８Ｂが、回転軸Ｘ方向から挿入されている。
　ドライブシャフト８Ｂは、モータ２のモータシャフト２０の内径側と中空軸５０の内径側を、回転軸Ｘ方向に横切って設けられており、ドライブシャフト８Ｂの先端側が、支持部６０１で回転可能に支持されている。 As shown in FIG. 1, a drive shaft 8B penetrating the opening 114 of the cover 11 is inserted into the support portion 601 of the differential case 60 from the rotation axis X direction.
The drive shaft 8B is provided so as to cross the inner diameter side of the motor shaft 20 of the motor 2 and the inner diameter side of the hollow shaft 50 in the rotation axis X direction, and the tip end side of the drive shaft 8B is rotatably supported by the support portion 601. Has been done.
　カバー１１の開口部１１４の内周には、リップシールＲＳが固定されており、リップシールＲＳの図示しないリップ部が、ドライブシャフト８Ｂの外周に弾発的に接触することで、ドライブシャフト８Ｂの外周と開口部１１４の内周との隙間が封止されている。 A lip seal RS is fixed to the inner circumference of the opening 114 of the cover 11, and the lip portion (not shown) of the lip seal RS elastically contacts the outer circumference of the drive shaft 8B, so that the drive shaft 8B has a lip seal RS. The gap between the outer circumference and the inner circumference of the opening 114 is sealed.
　図３に示すように、デフケース６０の内部では、ドライブシャフト８Ａ、８Ｂの先端部の外周に、サイドギア６３Ａ、６３Ｂがスプライン嵌合しており、サイドギア６３Ａ、６３Ｂとドライブシャフト８（８Ａ、８Ｂ）とが、回転軸Ｘ周りに一体回転可能に連結されている。 As shown in FIG. 3, inside the differential case 60, side gears 63A and 63B are spline-fitted on the outer periphery of the tip portions of the drive shafts 8A and 8B, and the side gears 63A and 63B and the drive shaft 8 (8A and 8B) are fitted. Are rotatably connected around the rotation shaft X.
　デフケース６０には、回転軸Ｘに直交する方向に貫通した軸孔６０ａ、６０ｂが、回転軸Ｘを挟んで対称となる位置に設けられている。
　軸孔６０ａ、６０ｂは、回転軸Ｘに直交する軸線Ｙ上に位置しており、シャフト６１の一端６１ａ側および他端６１ｂ側が挿入されている。 The differential case 60 is provided with shaft holes 60a and 60b penetrating in a direction orthogonal to the rotation axis X at positions symmetrical with respect to the rotation axis X.
The shaft holes 60a and 60b are located on the axis Y orthogonal to the rotation axis X, and one end 61a side and the other end 61b side of the shaft 61 are inserted.
　シャフト６１の一端６１ａ側および他端６１ｂ側は、ピンＰでデフケース６０に固定されており、シャフト６１は、軸線Ｙ周りの自転が禁止されている。
　シャフト６１は、デフケース６０内において、サイドギア６３Ａ、６３Ｂの間に位置しており、軸線Ｙに沿って配置されている。 One end 61a side and the other end 61b side of the shaft 61 are fixed to the differential case 60 by a pin P, and the shaft 61 is prohibited from rotating around the axis Y.
The shaft 61 is located between the side gears 63A and 63B in the differential case 60, and is arranged along the axis Y.
　デフケース６０内においてシャフト６１には、かさ歯車６２Ａ、６２Ｂが外挿して回転可能に支持されている。
　かさ歯車６２Ａ、６２Ｂは、シャフト６１の長手方向（軸線Ｙの軸方向）で間隔を空けて２つ設けられており、かさ歯車６２Ａ、６２Ｂは、互いの歯部を対向させた状態で配置されている。
　シャフト６１においてかさ歯車６２Ａ、６２Ｂは、当該かさ歯車６２Ａ、６２Ｂの軸心を、シャフト６１の軸心と一致させて設けられている。 In the differential case 60, bevel gears 62A and 62B are externally inserted and rotatably supported on the shaft 61.
Two bevel gears 62A and 62B are provided at intervals in the longitudinal direction of the shaft 61 (the axial direction of the axis Y), and the bevel gears 62A and 62B are arranged so that their teeth face each other. ing.
In the shaft 61, the bevel gears 62A and 62B are provided so that the axes of the bevel gears 62A and 62B are aligned with the axes of the shaft 61.
　デフケース６０内において、回転軸Ｘ方向におけるかさ歯車６２Ａ、６２Ｂの両側には、サイドギア６３Ａ、６３Ｂが位置している。
　サイドギア６３Ａ、６３Ｂは、互いの歯部を対向させた状態で、回転軸Ｘ方向に間隔を空けて２つ設けられており、かさ歯車６２Ａ、６２Ｂとサイドギア６３Ａ、６３Ｂとは、互いの歯部を噛合させた状態で組み付けられている。 In the differential case 60, side gears 63A and 63B are located on both sides of the bevel gears 62A and 62B in the rotation axis X direction.
Two side gears 63A and 63B are provided with their teeth facing each other at intervals in the X direction of the rotation axis, and the bevel gears 62A and 62B and the side gears 63A and 63B have teeth of each other. Is assembled in a meshed state.
　デフケース６０の下部側は、ケース１３内の潤滑油に浸っている。
　実施の形態では、シャフト６１の一端６１ａまたは他端６１ｂが最も下部側に位置した際に、シャフト６１の一端６１ａまたは他端６１ｂが少なくとも潤滑油内に位置する高さまで、ケース１３内に潤滑油が貯留されている。 The lower side of the differential case 60 is immersed in the lubricating oil inside the case 13.
In the embodiment, when one end 61a or the other end 61b of the shaft 61 is located on the lowermost side, the lubricating oil is contained in the case 13 until the height at which one end 61a or the other end 61b of the shaft 61 is located at least in the lubricating oil. Is stored.
　かかる構成の動力伝達装置１の作用を説明する。
　動力伝達装置１では、モータ２の出力回転の伝達経路に沿って、遊星減速ギア５と、差動装置６と、ドライブシャフト８（８Ａ、８Ｂ）と、が設けられている。 The operation of the power transmission device 1 having such a configuration will be described.
In the power transmission device 1, a planetary reduction gear 5, a differential device 6, and drive shafts 8 (8A, 8B) are provided along the transmission path of the output rotation of the motor 2.
　モータ２の駆動により、ロータコア２１が回転軸Ｘ回りに回転すると、ロータコア２１と一体に回転するモータシャフト２０を介して、遊星減速ギア５のサンギア５１（中空軸５０）に回転が入力される。 When the rotor core 21 rotates around the rotation shaft X by driving the motor 2, the rotation is input to the sun gear 51 (hollow shaft 50) of the planetary reduction gear 5 via the motor shaft 20 that rotates integrally with the rotor core 21.
　遊星減速ギア５では、サンギア５１が、遊星減速ギア５の出力回転の入力部となっており、段付きピニオンギア５３を支持するキャリア５５が、入力された回転の出力部となっている。 In the planetary reduction gear 5, the sun gear 51 is an input unit for the output rotation of the planetary reduction gear 5, and the carrier 55 that supports the stepped pinion gear 53 is an output unit for the input rotation.
　サンギア５１が入力された回転で回転軸Ｘ回りに回転すると、段付きピニオンギア５３（大径歯車部５３１、小径歯車部５３２）が、サンギア５１側から入力される回転で、軸線Ｘ１回りに回転する。
　ここで、段付きピニオンギア５３の小径歯車部５３２は、ケース１３の内周に固定されたリングギア５２に噛合している。そのため、段付きピニオンギア５３は、軸線Ｘ１回りに自転しながら、回転軸Ｘ周りに回転する。 When the sun gear 51 rotates around the rotation axis X by the input rotation, the stepped pinion gear 53 (large diameter gear portion 531 and small diameter gear portion 532) rotates around the axis X1 by the rotation input from the sun gear 51 side. To do.
Here, the small-diameter gear portion 532 of the stepped pinion gear 53 meshes with the ring gear 52 fixed to the inner circumference of the case 13. Therefore, the stepped pinion gear 53 rotates around the rotation axis X while rotating around the axis X1.
　ここで、段付きピニオンギア５３では、小径歯車部５３２の外径Ｒ２が大径歯車部５３１の外径Ｒ１よりも小さくなっている（図３参照）。
　これにより、段付きピニオンギア５３を支持するキャリア５５（側板部５５１、６５１）が、モータ２側から入力された回転よりも低い回転速度で回転軸Ｘ回りに回転する。
　そのため、遊星減速ギア５のサンギア５１に入力された回転は、段付きピニオンギア５３により、大きく減速されたのちに、キャリア５５の側板部６５１が一体に形成されたデフケース６０（差動装置６）に出力される。 Here, in the stepped pinion gear 53, the outer diameter R2 of the small diameter gear portion 532 is smaller than the outer diameter R1 of the large diameter gear portion 531 (see FIG. 3).
As a result, the carriers 55 (side plate portions 551 and 651) that support the stepped pinion gear 53 rotate around the rotation axis X at a rotation speed lower than the rotation input from the motor 2 side.
Therefore, the rotation input to the sun gear 51 of the planetary reduction gear 5 is greatly reduced by the stepped pinion gear 53, and then the side plate portion 651 of the carrier 55 is integrally formed with the differential case 60 (differential device 6). Is output to.
　そして、デフケース６０が入力された回転で回転軸Ｘ回りに回転することにより、ドライブシャフト８（８Ａ、８Ｂ）が回転軸Ｘ回りに回転して、動力伝達装置１が搭載された車両の左右の駆動輪（図示せず）に伝達される。 Then, when the differential case 60 rotates around the rotation axis X by the input rotation, the drive shafts 8 (8A, 8B) rotate around the rotation axis X, and the left and right sides of the vehicle on which the power transmission device 1 is mounted are left and right. It is transmitted to the drive wheels (not shown).
　ここで、動力伝達装置１では、デフケース６０の支持部６０１が、中空軸５０の内径Ｒ４よりも小さい外径Ｒ３で形成されており、デフケース６０の支持部６０１は、中空軸５０の内周に挿入されている。
　そのため、回転軸Ｘの径方向から見ると、中空軸５０のサンギア５１側も一部と、デフケース６０の支持部６０１とが、重なるよう配置される。これにより、中空軸５０とデフケース６０の支持部６０１とが回転軸Ｘ方向で重なった長さ分Ｌｘだけ、動力伝達装置１の回転軸Ｘ方向（軸長方向）の長さを短くできる。 Here, in the power transmission device 1, the support portion 601 of the differential case 60 is formed with an outer diameter R3 smaller than the inner diameter R4 of the hollow shaft 50, and the support portion 601 of the differential case 60 is formed on the inner circumference of the hollow shaft 50. It has been inserted.
Therefore, when viewed from the radial direction of the rotating shaft X, a part of the hollow shaft 50 on the sun gear 51 side and the support portion 601 of the differential case 60 are arranged so as to overlap each other. As a result, the length of the power transmission device 1 in the rotation axis X direction (axis length direction) can be shortened by the length Lx at which the hollow shaft 50 and the support portion 601 of the differential case 60 overlap in the rotation axis X direction.
　ここで、支持部６０１と中空軸５０とが略同じ外径で形成されている場合には、動力伝達装置１の回転軸Ｘ方向の長さを短くするために、支持部６０１の回転軸Ｘ方向の長さを短くする必要がある。 Here, when the support portion 601 and the hollow shaft 50 are formed to have substantially the same outer diameter, the rotation shaft X of the support portion 601 is used in order to shorten the length of the power transmission device 1 in the rotation shaft X direction. It is necessary to shorten the length in the direction.
　本実施形態では、デフケース６０の支持部６０１を中空軸５０の内周に挿入して配置することで、動力伝達装置１の回転軸Ｘ方向の長さを抑えつつ、ドライブシャフト８Ｂを支持する支持部６０１の長さを確保している。
　特に、デフケース６０の支持部６０１の内周は、当該支持部６０１に挿入されたドライブシャフト８Ｂを回転可能に支持しており、支持部６０１の外周は、ニードルベアリングＮＢを介して、中空軸５０のサンギア５１側の内周で回転可能に支持されている。
　そのため、ドライブシャフト８Ｂの支持安定性を確保しつつ、動力伝達装置１の回転軸Ｘ方向の長さを抑えている。 In the present embodiment, the support portion 601 of the differential case 60 is inserted into the inner circumference of the hollow shaft 50 and arranged to support the drive shaft 8B while suppressing the length of the power transmission device 1 in the rotation axis X direction. The length of the part 601 is secured.
In particular, the inner circumference of the support portion 601 of the differential case 60 rotatably supports the drive shaft 8B inserted in the support portion 601 and the outer circumference of the support portion 601 is the hollow shaft 50 via the needle bearing NB. It is rotatably supported on the inner circumference of the sun gear 51 side.
Therefore, the length of the power transmission device 1 in the rotation axis X direction is suppressed while ensuring the support stability of the drive shaft 8B.
　以上の通り、本実施形態にかかる動力伝達装置１は、以下の構成を有している。
（１）動力伝達装置１は、
　中空軸５０と、
　中空軸５０の下流に遊星減速ギア５（減速ギア）を介して接続された差動装置６（デファレンシャルギア）と、
　差動装置６の下流に接続されたドライブシャフト８（８Ａ、８Ｂ）と、
　を有する。
　ドライブシャフト８Ｂは、中空軸５０を貫通して配置されている。
　差動装置６のデフケース６０（デファレンシャルケース）は、ドライブシャフト８Ｂを支持する支持部６０１を有する。
　デフケース６０の支持部６０１は、中空軸５０の内周に挿入されている。 As described above, the power transmission device 1 according to the present embodiment has the following configuration.
(1) The power transmission device 1 is
Hollow shaft 50 and
A differential device 6 (differential gear) connected to the downstream of the hollow shaft 50 via a planetary reduction gear 5 (reduction gear),
Drive shafts 8 (8A, 8B) connected downstream of the differential device 6 and
Have.
The drive shaft 8B is arranged so as to penetrate the hollow shaft 50.
The differential case 60 (differential case) of the differential device 6 has a support portion 601 that supports the drive shaft 8B.
The support portion 601 of the differential case 60 is inserted into the inner circumference of the hollow shaft 50.
　デフケース６０でドライブシャフト８（８Ａ、８Ｂ）を支持する場合、ドライブシャフト８（８Ａ、８Ｂ）の支持安定性のために、支持部６０１、６０２の回転軸Ｘ方向の長さが、所定以上あることが好ましい。
　しかし、中空軸５０と支持部６０１の径が略同じであると、中空軸５０と支持部６０１とが干渉するために、動力伝達装置１の軸長方向（回転軸Ｘ方向）の短縮の妨げとなる。
　そこで、支持部６０１の外径を、中空軸５０内に挿入可能な外径Ｒ３に設定した。これにより、ドライブシャフト８Ｂの支持部６０１での支持安定性を確保しつつ、かつ、デフケース６０を中空軸５０側に寄せて配置することができるので、動力伝達装置１の軸長方向の短縮が可能となる。 When the drive shaft 8 (8A, 8B) is supported by the differential case 60, the lengths of the support portions 601 and 602 in the rotation axis X direction are longer than a predetermined length for the support stability of the drive shaft 8 (8A, 8B). Is preferable.
However, if the diameters of the hollow shaft 50 and the support portion 601 are substantially the same, the hollow shaft 50 and the support portion 601 interfere with each other, which hinders the shortening of the power transmission device 1 in the axial length direction (rotation axis X direction). It becomes.
Therefore, the outer diameter of the support portion 601 is set to the outer diameter R3 that can be inserted into the hollow shaft 50. As a result, the support stability of the drive shaft 8B at the support portion 601 can be ensured, and the differential case 60 can be arranged closer to the hollow shaft 50 side, so that the power transmission device 1 can be shortened in the axial length direction. It will be possible.
　本実施形態にかかる動力伝達装置１は、以下の構成を有している。
（２）支持部６０１は、ニードルベアリングＮＢ（軸受）を介して、中空軸５０の内周に支持されている。 The power transmission device 1 according to the present embodiment has the following configuration.
(2) The support portion 601 is supported on the inner circumference of the hollow shaft 50 via a needle bearing NB (bearing).
　ニードルベアリングＮＢ（軸受）を、中空軸５０の内周側に設けることで、中空軸５０とデフケース６０の支持部６０１とが、回転軸Ｘの径方向から見て重なるように設けることができる。これにより、デフケース６０と中空軸５０との径方向における干渉を防止することができる。
　なお、前記した実施形態では、支持部６０１が、ニードルベアリングＮＢ（軸受）を介して中空軸５０の内周に支持されている場合を例示した。ニードルベアリングＮＢに代えて、円環状のブッシュを設けて、支持部６０１が、ブッシュを介して中空軸５０の内周に支持されている構成としても良い。
　ここで、ブッシュとは、例えば、中空軸と支持部との相対回転を許容する金属の環である。
　また、軸方向から視たときにおいて中空軸５０とデフケース６０との間にスラスト軸受としてのニードルベアリングＮＢを配置しない場合は軸方向の短縮化が可能となる。
　言い換えると、軸方向において中空軸５０とデフケース６０との間にクリアランスを設けることにより、軸方向の短縮化が可能となる。 By providing the needle bearing NB (bearing) on the inner peripheral side of the hollow shaft 50, the hollow shaft 50 and the support portion 601 of the differential case 60 can be provided so as to overlap each other when viewed from the radial direction of the rotating shaft X. As a result, it is possible to prevent the differential case 60 and the hollow shaft 50 from interfering with each other in the radial direction.
In the above-described embodiment, the case where the support portion 601 is supported on the inner circumference of the hollow shaft 50 via the needle bearing NB (bearing) is illustrated. Instead of the needle bearing NB, an annular bush may be provided so that the support portion 601 is supported on the inner circumference of the hollow shaft 50 via the bush.
Here, the bush is, for example, a metal ring that allows relative rotation between the hollow shaft and the support portion.
Further, when the needle bearing NB as a thrust bearing is not arranged between the hollow shaft 50 and the differential case 60 when viewed from the axial direction, the axial direction can be shortened.
In other words, by providing a clearance between the hollow shaft 50 and the differential case 60 in the axial direction, the axial direction can be shortened.
　本実施形態にかかる動力伝達装置１は、以下の構成を有している。
（３）動力伝達装置１におけるモータ２の出力回転の伝達経路では、中空軸５０の上流にモータ２が接続されている。
　ドライブシャフト８Ｂは、モータ２の内周を貫通して配置されている。 The power transmission device 1 according to the present embodiment has the following configuration.
(3) In the transmission path of the output rotation of the motor 2 in the power transmission device 1, the motor 2 is connected upstream of the hollow shaft 50.
The drive shaft 8B is arranged so as to penetrate the inner circumference of the motor 2.
　筒状のモータシャフト２０を貫通して、ドライブシャフト８Ｂを配置することで、動力伝達装置１の縦方向（重力方向）にダウンサイジングが可能である。 By arranging the drive shaft 8B through the tubular motor shaft 20, it is possible to downsize the power transmission device 1 in the vertical direction (gravity direction).
　図４は、変形例にかかる動力伝達装置１Ａの差動装置６周りの拡大図である。
　前記した実施形態では、中空軸５０のデフケース６０側の端部５０ａが、デフケース６０の側縁部６０ｃに、回転軸Ｘ方向の隙間をあけて対向している場合を例示した（図３参照）。
　ここで、図４に示すように、中空軸５０のデフケース６０側の端部５０ａと、デフケース６０の側縁部６０ｃとの間に、ニードルベアリングＮＢ（スラスト軸受）を設けた構成としても良い。
　このように構成すると、中空軸５０に、デフケース６０側に近づける方向の押しつけ力が作用した場合に、中空軸５０とデフケース６０とが直接接触することを好適に防止できる。中空軸５０とデフケース６０とが接触すると、モータ２の出力回転の伝達経路におけるトルク伝達に対する抵抗となり、動力伝達装置１Ａを搭載した車両の電費に影響が生ずるが、かかる事態の発生を好適に防止できる。 FIG. 4 is an enlarged view of the power transmission device 1A around the differential device 6 according to the modified example.
In the above-described embodiment, the case where the end portion 50a of the hollow shaft 50 on the differential case 60 side faces the side edge portion 60c of the differential case 60 with a gap in the rotation axis X direction is exemplified (see FIG. 3). ..
Here, as shown in FIG. 4, a needle bearing NB (thrust bearing) may be provided between the end portion 50a of the hollow shaft 50 on the differential case 60 side and the side edge portion 60c of the differential case 60.
With this configuration, when a pressing force in the direction of approaching the differential case 60 acts on the hollow shaft 50, it is possible to preferably prevent the hollow shaft 50 and the differential case 60 from coming into direct contact with each other. When the hollow shaft 50 and the differential case 60 come into contact with each other, it becomes a resistance to torque transmission in the transmission path of the output rotation of the motor 2, which affects the electricity cost of the vehicle equipped with the power transmission device 1A, but preferably prevents such a situation from occurring. it can.
　ここで、本明細書における用語「下流に接続」とは、上流に配置された部品から下流に配置された部品へと動力が伝達される接続関係にあることを意味する。
　例えば、モータ２の下流に接続された遊星減速ギア５という場合は、モータ２から遊星減速ギア５へと動力が伝達されることを意味する。
　また、本明細書における用語「直接接続」とは、他の減速機構、増速機構、変速機構などの減速比が変換される部材を介さずに部材同士が動力伝達可能に接続されていることを意味する。 Here, the term "downstream connection" in the present specification means that there is a connection relationship in which power is transmitted from a component arranged upstream to a component arranged downstream.
For example, the case of the planetary reduction gear 5 connected downstream of the motor 2 means that power is transmitted from the motor 2 to the planetary reduction gear 5.
Further, the term "direct connection" in the present specification means that the members are connected so as to be able to transmit power without the intervention of other members such as a reduction mechanism, a speed increase mechanism, and a transmission mechanism whose reduction ratio is converted. Means.
　前記した実施形態では、段付きピニオンギア５３を採用した遊星減速ギア５を例示したが、段付きでないピニオンギアを採用した遊星減速ギアを採用しても良い。 In the above-described embodiment, the planetary reduction gear 5 adopting the stepped pinion gear 53 is illustrated, but the planetary reduction gear adopting the non-stepped pinion gear may be adopted.
　なお、モータ２の出力部（モータシャフト２０）と遊星減速ギア５の入力部（サンギア５１）との連結態様は、前記した実施形態のものに限定されない。
　モータ２の出力部（モータシャフト２０）と遊星減速ギア５の入力部（サンギア５１）とを、別のギア部品などを介して回転伝達可能に連結した構成としても良い。 The connection mode between the output unit (motor shaft 20) of the motor 2 and the input unit (sun gear 51) of the planetary reduction gear 5 is not limited to that of the above-described embodiment.
The output unit (motor shaft 20) of the motor 2 and the input unit (sun gear 51) of the planetary reduction gear 5 may be connected to each other so that rotation can be transmitted via another gear component or the like.
　さらに、実施形態では、減速機構が、段付きピニオンギア５３を備える遊星減速ギア５であり、モータ２の出力回転の伝達経路上に、ひとつの遊星減速ギア５が設けられている場合を例示した。
　本発明は、この態様にのみに限定されない。モータ２の出力回転の伝達経路上に、複数の遊星減速ギアが直列に配置されている構成としても良い。 Further, in the embodiment, the case where the reduction mechanism is a planetary reduction gear 5 including a stepped pinion gear 53 and one planetary reduction gear 5 is provided on the transmission path of the output rotation of the motor 2 is illustrated. ..
The present invention is not limited to this aspect. A plurality of planetary reduction gears may be arranged in series on the transmission path of the output rotation of the motor 2.
　以上、本願発明の実施形態を説明したが、本願発明は、これら実施形態に示した態様のみに限定されるものではない。発明の技術的な思想の範囲内で、適宜変更可能である。 Although the embodiments of the present invention have been described above, the present invention is not limited to the embodiments shown in these embodiments. It can be changed as appropriate within the scope of the technical idea of the invention.

Claims (3)

  1. 　中空軸と、
    　前記中空軸の下流に減速ギアを介して接続されたデファレンシャルギアと、
    　前記デファレンシャルギアの下流に接続されたドライブシャフトと、を有し、
    　前記ドライブシャフトは、前記中空軸を貫通して配置されており、
    　前記デファレンシャルギアのデファレンシャルケースは前記ドライブシャフトを支持する支持部を有し、
    　前記デファレンシャルケースの前記支持部は、前記中空軸の内周に挿入されている、動力伝達装置。     Hollow shaft and
    A differential gear connected to the downstream of the hollow shaft via a reduction gear,
    With a drive shaft connected downstream of the differential gear,
    The drive shaft is arranged so as to penetrate the hollow shaft.
    The differential case of the differential gear has a support portion for supporting the drive shaft.
    The support portion of the differential case is a power transmission device inserted into the inner circumference of the hollow shaft.
  2. 　請求項１に記載の動力伝達装置において、
    　前記支持部は、軸受又はブッシュを介して前記中空軸の内周に支持されている、動力伝達装置。     In the power transmission device according to claim 1,
    The support portion is a power transmission device supported on the inner circumference of the hollow shaft via a bearing or a bush.
  3. 　請求項１又は請求項２に記載の動力伝達装置において、
    　前記中空軸の上流にモータが接続され、
    　前記ドライブシャフトは、前記モータの内周を貫通して配置されている、動力伝達装置。     In the power transmission device according to claim 1 or 2.
    A motor is connected upstream of the hollow shaft,
    The drive shaft is a power transmission device arranged so as to penetrate the inner circumference of the motor.
PCT/JP2019/047106 2019-03-10 2019-12-03 Power transmission device WO2020183815A1 (en)

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JP2019-043241 2019-03-10
JP2019043241A JP2022074169A (en) 2019-03-10 2019-03-10 Power transmission device

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11257463A (en) * 1998-03-06 1999-09-21 Zexel:Kk Parallel shaft differential gear device
JP2005133758A (en) * 2003-10-28 2005-05-26 Toyoda Mach Works Ltd Power transmitting device for vehicles
JP2013029195A (en) * 2011-06-24 2013-02-07 Jtekt Corp Motor driving force transmission device
WO2018147161A1 (en) * 2017-02-08 2018-08-16 武蔵精密工業株式会社 Power transmitting device
WO2019039599A1 (en) * 2017-08-25 2019-02-28 アイシン・エィ・ダブリュ株式会社 Vehicle drive device

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11257463A (en) * 1998-03-06 1999-09-21 Zexel:Kk Parallel shaft differential gear device
JP2005133758A (en) * 2003-10-28 2005-05-26 Toyoda Mach Works Ltd Power transmitting device for vehicles
JP2013029195A (en) * 2011-06-24 2013-02-07 Jtekt Corp Motor driving force transmission device
WO2018147161A1 (en) * 2017-02-08 2018-08-16 武蔵精密工業株式会社 Power transmitting device
WO2019039599A1 (en) * 2017-08-25 2019-02-28 アイシン・エィ・ダブリュ株式会社 Vehicle drive device

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