WO2023188621A1 - Drive device - Google Patents

Drive device Download PDF

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Publication number
WO2023188621A1
WO2023188621A1 PCT/JP2022/047298 JP2022047298W WO2023188621A1 WO 2023188621 A1 WO2023188621 A1 WO 2023188621A1 JP 2022047298 W JP2022047298 W JP 2022047298W WO 2023188621 A1 WO2023188621 A1 WO 2023188621A1
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WO
WIPO (PCT)
Prior art keywords
shaft
bearing
flow path
drive device
peripheral surface
Prior art date
Application number
PCT/JP2022/047298
Other languages
French (fr)
Japanese (ja)
Inventor
優海 杉野
直大 和田
祐輔 牧野
啓介 麻生
祥平 大菅
Original Assignee
ニデック株式会社
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 ニデック株式会社 filed Critical ニデック株式会社
Publication of WO2023188621A1 publication Critical patent/WO2023188621A1/en

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    • 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
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears

Definitions

  • the present invention relates to a drive device.
  • This application claims priority based on Japanese Patent Application No. 2022-061136 filed in Japan on March 31, 2022, the contents of which are incorporated herein.
  • Patent Document 1 discloses a structure in which the shafts on the motor side and the speed reducer side are hollow shafts, and oil is supplied to the connecting portion by flowing oil into the hollow shafts.
  • the fluid used for lubrication may also be used to cool the motor. In this case, it is necessary to send fluid from the gear chamber to the motor chamber, but if a new flow path is provided in addition to the flow path for lubricating the connecting portion, there is a problem in that the structure of the flow path becomes complicated.
  • one object of the present invention is to provide a drive device that can move fluid between a motor chamber and a gear chamber while supplying fluid to a connecting portion of a shaft.
  • One aspect of the drive device of the present invention includes a rotor having a first shaft that rotates around a central axis, a motor having a stator surrounding the rotor, a plurality of gears, and a first shaft that rotates around the central axis.
  • a housing that has two shafts and is provided with a power transmission section that transmits the power of the motor, a motor chamber that accommodates the motor, and a gear chamber that accommodates the power transmission section; and a housing that supports the first shaft.
  • the housing has a partition wall that partitions the motor chamber and the gear chamber.
  • the partition wall is provided with a communication hole that communicates the motor chamber and the gear chamber. The inner peripheral surface of the communication hole holds the first bearing and the second bearing.
  • connection space in which the connection opening opens is provided between the first bearing and the second bearing in the communication hole in the axial direction.
  • the flow path includes a first flow path that connects the gear chamber and the connection space, and a second flow path that connects the connection space and the motor chamber.
  • a drive device that can move fluid between a motor chamber and a gear chamber while supplying fluid to a connecting portion of a shaft.
  • FIG. 1 is a conceptual diagram of a drive device according to an embodiment.
  • FIG. 2 is a front view of the gear chamber of one embodiment viewed from one side in the axial direction.
  • FIG. 3 is a rear view of the gear chamber of one embodiment viewed from the other axial side.
  • FIG. 4 is a cross-sectional view of a connecting portion of a first shaft and a second shaft in one embodiment.
  • FIG. 5 is a partial cross-sectional view of a coupling portion of one embodiment.
  • FIG. 6 is a cross-sectional view of a connecting portion of a first shaft and a second shaft in a modified example.
  • FIG. 7 is a sectional view showing a connecting portion between the first shaft and the second shaft of the second embodiment.
  • an XYZ coordinate system is appropriately shown as a three-dimensional orthogonal coordinate system.
  • the Z-axis direction indicates the vertical direction (that is, the up-down direction), the +Z direction is the upper side (opposite to the direction of gravity), and the -Z direction is the lower side (the direction of gravity).
  • the X-axis direction is a direction orthogonal to the Z-axis direction, and indicates the front-rear direction of the vehicle in which the drive device 1 is mounted.
  • the side to which the X-axis arrow points (+X side) is the front side of the vehicle, and the side opposite to the side to which the X-axis arrow points (-X side) is the rear side of the vehicle.
  • the Y-axis direction is a direction perpendicular to both the X-axis direction and the Z-axis direction, and indicates the width direction (left-right direction) of the vehicle.
  • the side to which the Y-axis arrow points (+Y side) is the left side of the vehicle, and the side opposite to the side to which the Y-axis arrow points (-Y side) is the right side of the vehicle.
  • the front-rear direction and the left-right direction are horizontal directions perpendicular to the vertical direction.
  • the direction parallel to the central axis J1 of the motor 2 (Y-axis direction) is simply referred to as the "axial direction", and the radial direction centered on the central axis J1 is simply referred to as the "radial direction”.
  • the circumferential direction centered on the central axis J1, that is, the circumferential direction around the central axis J1 is simply referred to as the "circumferential direction.”
  • the above-mentioned "parallel direction” also includes substantially parallel directions.
  • the -Y direction may be simply referred to as one axial direction
  • the +Y direction may simply be referred to as the other axial direction.
  • FIG. 1 is a conceptual diagram of a drive device 1 according to the first embodiment.
  • the drive device 1 of this embodiment is mounted on a vehicle that uses a motor as a power source, such as a hybrid vehicle (HEV), a plug-in hybrid vehicle (PHV), or an electric vehicle (EV), and is used as the power source.
  • a motor such as a hybrid vehicle (HEV), a plug-in hybrid vehicle (PHV), or an electric vehicle (EV)
  • the drive device 1 includes a motor 2, a power transmission section 4, a housing 6, and a plurality of bearings 5A, 5B, 5C, 5D, 5E, 5F, 5G, and 5H.
  • Housing 6 accommodates motor 2, power transmission section 4, and a plurality of bearings 5A to 5H.
  • the plurality of bearings 5A to 5H are respectively referred to as a first bearing 5A, a second bearing 5B, a third bearing 5C, a fourth bearing 5D, a fifth bearing 5E, a sixth bearing 5F, a seventh bearing 5G, and It may be called the eighth bearing 5H.
  • the motor 2 of this embodiment is an inner rotor type three-phase AC motor. Note that the configuration of the motor 2 is not limited to this embodiment, and may be, for example, a four-phase or more AC motor.
  • the motor 2 is arranged in the motor chamber R1 of the housing 6.
  • the motor 2 includes a rotor 20 and a stator 30 that faces the rotor 20 in the radial direction.
  • the motor 2 of this embodiment is an inner rotor type motor in which a rotor 20 is arranged inside a stator 30.
  • the rotor 20 rotates around a central axis J1 that extends in the horizontal direction.
  • the rotor 20 includes a first shaft 21, a rotor core 24 fixed to the outer peripheral surface of the first shaft 21, and a rotor magnet (not shown) fixed to the rotor core 24.
  • the torque of the rotor 20 is transmitted to the power transmission section 4.
  • the first shaft 21 extends in the axial direction centering on the central axis J1.
  • the first shaft 21 rotates around the central axis J1. Both ends of the first shaft 21 are rotatably supported by a first bearing 5A and a third bearing 5C.
  • the first shaft 21 is a cylindrical hollow shaft.
  • the inside of the first shaft 21 will be referred to as a hollow portion 21H.
  • the hollow portion 21H of the first shaft 21 opens on one axial side (-Y side) and the other axial side (+Y side).
  • the first shaft 21 is provided with a through hole 21h that penetrates in the radial direction.
  • a plurality of through holes 21h are provided at intervals in the circumferential direction.
  • the rotor core 24 is provided with an internal rotor flow path 24H that is connected to the through hole 21h.
  • fluid O flows into the hollow portion 21H from an opening on one side in the axial direction ( ⁇ Y side).
  • the fluid O in the hollow portion 21H passes through the through hole 21h and the rotor internal flow path 24H and scatters onto the stator 30 due to the centrifugal force caused by the rotation of the rotor 20.
  • Fluid O cools rotor 20 and stator 30.
  • the fluid O in the hollow portion 21H leaks from the other axial side (+Y side) and lubricates the third bearing 5C.
  • the stator 30 is held in the housing 6.
  • the stator 30 surrounds the rotor 20 from the outside in the radial direction.
  • the stator 30 includes an annular stator core 32 centered on the central axis J1, a coil 31 attached to the stator core 32, and an insulator (not shown) interposed between the stator core 32 and the coil 31.
  • the stator core 32 has a plurality of magnetic pole teeth (not shown) radially inward from the inner peripheral surface of the annular yoke.
  • a coil wire is arranged between the magnetic pole teeth.
  • the coil wire located within the gap between adjacent magnetic pole teeth constitutes the coil 31.
  • the insulator is made of an insulating material.
  • the power transmission section 4 is arranged on one axial side (-Y side) with respect to the motor 2.
  • the power transmission section 4 is connected to the rotor 20 and transmits the power of the motor 2, and outputs the power to the output shaft 47.
  • the power transmission section 4 includes a reduction gear 4a and a differential gear 4b. That is, the drive device 1 includes a speed reduction device 4a and a differential device 4b.
  • the differential device 4b in which the rotational axes of the respective gears are arranged in parallel, transmits the same torque to both the left and right wheels while absorbing the speed difference between the left and right wheels when the vehicle turns.
  • the reduction gear 4a has a second shaft 44, a third shaft 45, a first gear 41, a second gear 42, and a third gear 43.
  • the differential device 4b includes a ring gear 46g, a differential case 46, and a differential mechanism section 46c disposed inside the differential case 46. That is, the power transmission section 4 includes a plurality of gears 41, 42, 43, 46g and a plurality of shafts 44, 45.
  • the second shaft 44 extends in the axial direction centering on the central axis J1.
  • the second shaft 44 is arranged coaxially with the first shaft 21.
  • the second shaft 44 is connected to the end of the first shaft 21 on the one axial side (-Y side) at the end on the other axial side (+Y side).
  • the second shaft 44 rotates together with the first shaft 21 about the central axis J1.
  • the second shaft 44 is rotatably supported by the second bearing 5B and the fourth bearing 5D.
  • the first gear 41 is provided on the outer peripheral surface of the second shaft 44.
  • the first gear 41 rotates together with the second shaft 44 around the central axis J1.
  • the third shaft 45 rotates around an intermediate axis J2 that is parallel to the central axis J1.
  • the third shaft 45 is rotatably supported by the fifth bearing 5E and the sixth bearing 5F.
  • the second gear 42 and the third gear 43 are arranged side by side in the axial direction.
  • the second gear 42 and the third gear 43 are provided on the outer peripheral surface of the third shaft 45.
  • the second gear 42 and the third gear 43 are connected via a third shaft 45.
  • the second gear 42 and the third gear 43 rotate about the intermediate axis J2.
  • the second gear 42 meshes with the first gear 41.
  • the third gear 43 meshes with a ring gear 46g of the differential device 4b.
  • the first gear 41, the second gear 42, the third gear 43, and the ring gear 46g are each helical gears.
  • the ring gear 46g rotates around an output axis J3 that is parallel to the central axis J1. Torque output from the motor 2 is transmitted to the ring gear 46g via the reduction gear 4a. Ring gear 46g is fixed to differential case 46.
  • the differential case 46 includes a case portion 46b that accommodates a differential mechanism portion 46c therein, and a differential case shaft 46a that protrudes to the other side and the other side in the axial direction with respect to the case portion 46b. That is, the power transmission section 4 includes a differential case shaft 46a.
  • the differential case shaft 46a has a cylindrical shape that extends in the axial direction centering on the output axis J3.
  • the differential case shaft 46a is rotatably supported by a seventh bearing 5G and an eighth bearing 5H.
  • Ring gear 46g is provided on the outer peripheral surface of differential case shaft 46a. The differential case shaft 46a rotates together with the ring gear 46g about the output axis J3.
  • the pair of output shafts 47 are connected to the differential gear 4b.
  • the pair of output shafts 47 protrude from the differential case 46 of the differential device 4b to the other side in the axial direction and to the other side.
  • the output shaft 47 is arranged inside the differential case shaft 46a.
  • the output shaft 47 is rotatably supported on the inner peripheral surface of the differential case shaft 46a via a bearing (not shown).
  • the torque output from the motor 2 is transmitted to the ring gear 46g of the differential device 4b via the second shaft 44, first gear 41, second gear 42, third shaft 45, and third gear 43 of the motor 2, It is output to the output shaft 47 via the differential mechanism section 46c of the differential device 4b.
  • the plurality of gears 41, 42, 43, and 46g of the power transmission section 4 transmit the power of the motor 2 to the second shaft 44, the third shaft 45, and the differential case shaft 46a in this order.
  • the housing 6 includes a motor cover 6A, a housing body 6B, a gear cover 6C, and a water jacket 6D.
  • the motor cover 6A, the housing body 6B, the gear cover 6C, and the water jacket 6D are each separate members.
  • the motor cover 6A is arranged on the other axial side (+Y side) of the housing body 6B.
  • the gear cover 6C is arranged on one axial side (-Y side) of the housing body 6B.
  • Water jacket 6D is arranged inside housing body 6B.
  • the housing main body 6B accommodates the motor 2 and opens on the other axial side (+Y side).
  • the housing main body 6B includes a cylindrical outer cylinder part 65 centered on the central axis J1, and an opening on one axial side of the outer cylinder part 65, which is arranged on one axial side (-Y side) of the outer cylinder part 65. It has a partition wall 65a that covers the partition wall 65a, and a first peripheral wall portion 65b extending from the outer edge of the partition wall 65a to one side in the axial direction (-Y side). That is, the housing 6 has a partition wall 65a.
  • a communication hole 65h is provided in the partition wall 65a.
  • a first bearing 5A, a second bearing 5B, and a seal member 5S are arranged inside the communication hole 65h.
  • the first shaft 21 and the second shaft 44 are connected to each other inside the communication hole 65h.
  • the seal member 5S in FIG. 1 is drawn schematically and does not reproduce the actual arrangement. The configuration of the communication hole 65h will be described in detail later based on FIG. 4.
  • the outer cylindrical portion 65 surrounds the motor 2 from the outside in the radial direction.
  • the outer cylindrical portion 65 supports the stator 30 via the water jacket 6D.
  • the gear cover 6C is arranged on one axial side (-Y side) of the housing body 6B.
  • the gear cover 6C includes an opposing wall 67 that faces the partition wall 65a, and a second peripheral wall portion 67a extending from the outer edge of the opposing wall 67 toward the other axial side (+Y side).
  • the end face of the second peripheral wall portion 67a on the other axial side (+Y side) is fastened to the end face of the first peripheral wall portion 65b on the one axial side ( ⁇ Y side).
  • the motor cover 6A covers the opening on the other axial side (+Y side) of the outer cylinder portion 65 of the housing body 6B.
  • the motor cover 6A holds a third bearing 5C that rotatably supports the rotor 20.
  • the water jacket 6D has a cylindrical inner cylinder part 64 centered on the central axis J1, and a protruding rib 64a provided on the outer peripheral surface of the inner cylinder part 64.
  • the inner cylinder portion 64 surrounds the stator 30 from the outside in the radial direction.
  • the inner diameter of the inner cylindrical portion 64 substantially matches the outer diameter of the stator core 32.
  • the inner circumferential surface of the inner cylindrical portion 64 contacts the outer circumferential surface of the stator 30. Moreover, the inner cylinder part 64 is surrounded by the outer cylinder part 65 from the outside in the radial direction. The outer diameter of the inner cylindrical portion 64 is smaller than the inner diameter of the outer cylindrical portion 65 of the housing body 6B. A gap is provided between the inner cylindrical portion 64 and the outer cylindrical portion 65, which functions as a water channel 93.
  • the protruding rib 64a extends spirally around the central axis J1.
  • the protruding rib 64a has a tip located at the radially outer end.
  • the tip of the protruding rib 64a contacts the inner circumferential surface of the outer cylindrical portion 65, or faces the inner circumferential surface of the outer cylindrical portion 65 with a slight gap therebetween.
  • the protruding rib 64a partitions the gap between the inner cylinder part 64 and the outer cylinder part 65, and makes the water channel 93 spiral.
  • the housing 6 is provided with a water channel 93 that extends along the outer peripheral surface of the stator 30. Cooling water L flows through the water channel 93 .
  • the cooling water L is, for example, water.
  • the stator 30 can be cooled by the cooling water L flowing through the water channel 93.
  • the water channel 93 extends in a spiral shape.
  • the water channel 93 is not limited to this embodiment as long as it surrounds the stator 30.
  • the water channel 93 may be a meandering channel in the axial direction or the circumferential direction.
  • the flow path configuration of the water channel 93 can be determined by the shape of the protruding rib 64a.
  • a motor chamber R1 that accommodates the motor 2 and a gear chamber R2 that accommodates the power transmission section 4 are provided inside the housing 6.
  • the motor chamber R1 and the gear chamber R2 are partitioned by a partition wall 65a.
  • the motor chamber R1 is a space surrounded from the outside in the radial direction by the outer cylinder portion 65 and sandwiched in the axial direction by the partition wall 65a and the motor cover 6A.
  • the gear chamber R2 is a space surrounded by the first circumferential wall portion 65b and the second circumferential wall portion 67a in the radial direction, and sandwiched between the partition wall 65a and the opposing wall 67 in the axial direction.
  • the gear chamber R2 is arranged on one axial side (-Y side) of the motor chamber R1.
  • a fluid O is stored in the gear chamber R2.
  • the fluid O is, for example, oil.
  • the fluid O is used as a lubricating oil for the power transmission section 4 and the bearings.
  • As the fluid O for example, in order to perform the functions of a refrigerant and a lubricant, it is preferable to use an oil equivalent to automatic transmission fluid (ATF), which has a relatively low viscosity.
  • ATF automatic transmission fluid
  • the housing 6 is provided with a fluid path 50 through which the fluid O passes.
  • fluid path means a path for the fluid O circulating within the housing 6. Therefore, the term “fluid path” refers not only to a tubular flow path that forms a steady flow of fluid O that constantly goes in one direction, but also to a path that temporarily retains fluid O (for example, a storage section), a fluid This concept also includes a path through which O drips and a path through which fluid O scatters.
  • the fluid path 50 includes a first raking path 58, a second raking path 59, a first supply path 51, a second supply path (flow path) 52, a third supply path 53, and a second raking path 59. It has a fourth supply flow path 54 and a fifth supply flow path 55. Further, a first storage section (catch tank) 84 and a second storage section 82 are arranged in the fluid path 50 . That is, the drive device 1 includes a first scraping path 58, a second scraping path 59, a first supply channel 51, a second supply channel 52, a third supply channel 53, a fourth supply channel 54, and a 5 supply channel 55, a first storage section 84, and a second storage section 82. Fluid O flows through the first supply channel 51 , the second supply channel 52 , the third supply channel 53 , the fourth supply channel 54 , and the fifth supply channel 55 . Further, fluid O is accumulated in the first storage section 84 and the second storage section 82 .
  • the first storage portion 84 is arranged in the gear chamber R2.
  • the first storage section 84 is a catch tank that opens upward.
  • the first storage section 84 receives the fluid O scooped up by each gear (for example, the ring gear 46g and the second gear 42) of the power transmission section 4.
  • FIG. 2 is a front view of the gear chamber R2 viewed from one axial side (-Y side).
  • FIG. 3 is a rear view of the gear chamber R2 viewed from the other axial side (+Y side).
  • the first storage portion 84 of this embodiment includes a first rib 84d that protrudes from the partition wall 65a to one axial side (-Y side), and a first rib 84d that protrudes from the opposite wall 67 to the other axial side (-Y side). +Y side).
  • One axial end surface of the first rib 84d and the other axial end surface of the second rib 84e contact and connect with each other.
  • the second storage portion 82 is a fluid reservoir provided in the lower region of the gear chamber R2. That is, the second storage section 82 in which the fluid O is stored is provided in the lower region of the gear chamber R2. A lower end of the ring gear 46g and a lower end of the second gear 42 are located within the second storage portion 82. Therefore, the ring gear 46g and a portion of the second gear 42 are immersed in the fluid O accumulated in the second storage section 82.
  • the first scooping path 58 scrapes up the fluid O in the second storage section 82 and transfers it to the first storage section 84 by the rotation of the gears of the power transmission section 4 (in this embodiment, the ring gear 46g and the second gear 42). It is a path that leads.
  • the amount of storage in the first storage section 84 increases, and the liquid level of the fluid O in the first storage section 84 increases. Go down.
  • the liquid level in the second storage part 82 can be lowered, and the stirring resistance of the ring gear 46g and the second gear 42 due to the fluid O can be reduced. can.
  • the second scooping path 59 scoops up the fluid O in the second storage section 82 and supplies it to the eighth bearing 5H by the rotation of the gears of the power transmission section 4 (in this embodiment, the ring gear 46g and the second gear 42). This is the route to
  • the first supply channel 51 and the third supply channel 53 are provided on the opposing wall 67 of the gear cover 6C.
  • the first supply channel 51 extends from the first storage section 84 toward the fourth bearing 5D.
  • the first supply channel 51 supplies the fluid O in the first storage section 84 to the fourth bearing 5D.
  • the third supply channel 53 extends from the first storage section 84 toward the sixth bearing 5F.
  • the third supply channel 53 supplies the fluid O in the first storage section 84 to the sixth bearing 5F.
  • the second supply channel 52, the fourth supply channel 54, and the fifth supply channel 55 are provided in the partition wall 65a of the housing body 6B.
  • the second supply channel 52 extends from the first storage section 84 toward the inner peripheral surface of the communication hole 65h. The configuration of the second supply channel 52 will be described in detail later.
  • the fourth supply flow path 54 extends from the first storage section 84 toward the fifth bearing 5E.
  • the fourth supply channel 54 supplies the fluid O in the first storage section 84 to the fifth bearing 5E.
  • the fifth supply channel 55 extends from the first storage section 84 toward the seventh bearing 5G.
  • the fifth supply channel 55 supplies the fluid O in the first storage section 84 to the seventh bearing 5G.
  • FIG. 4 is a sectional view of the first shaft 21 and the second shaft 44 arranged in the communication hole 65h.
  • the communication hole 65h communicates the motor chamber R1 and the gear chamber R2.
  • the inner circumferential surface of the communication hole 65h is circular centered on the central axis J1.
  • the inner peripheral surface of the communication hole 65h holds the first bearing 5A, the second bearing 5B, and the seal member 5S.
  • the partition wall 65a has a cylindrical portion 11 that protrudes toward the gear chamber R2 side (ie, one axial side (-Y side)) along the inner edge of the communication hole 65h.
  • the cylindrical portion 11 has a cylindrical shape centered on the central axis J1.
  • the cylindrical portion 11 surrounds and holds the first bearing 5A and the second bearing 5B.
  • the inner circumferential surface of the cylindrical portion 11 is the inner circumferential surface of the communication hole 65h.
  • the inner circumferential surface of the communication hole 65h includes a first inner circumferential surface 66a, a second inner circumferential surface 66b, a third inner circumferential surface 66c, a fourth inner circumferential surface 66d, a first stepped surface 66e, a second stepped surface 66f, and a third inner circumferential surface 66c. It has a three-step surface 66g.
  • the first inner circumferential surface 66a, the second inner circumferential surface 66b, the third inner circumferential surface 66c, and the fourth inner circumferential surface 66d extend from the other axial side (+Y side) to the one axial side (-Y side). Line up in the order of levers.
  • the first inner peripheral surface 66a surrounds the outer peripheral surface of the first bearing 5A.
  • the first inner peripheral surface 66a holds the first bearing 5A.
  • the diameter of the first inner peripheral surface 66a is larger than the diameter of the second inner peripheral surface 66b.
  • a first step surface 66e facing the other axial side (+Y side) is provided between the first inner circumferential surface 66a and the second inner circumferential surface 66b.
  • One axial end surface of the outer ring 5Aa of the first bearing 5A is pressed against the first stepped surface 66e.
  • the first bearing 5A supports the first shaft 21.
  • a seal member 5S is held on the second inner circumferential surface 66b.
  • the second inner peripheral surface 66b holds the seal member 5S.
  • the diameter of the second inner circumferential surface 66b is larger than the diameter of the third inner circumferential surface 66c. Therefore, there is a gap between the second inner circumferential surface 66b and the third inner circumferential surface 66c on the other side in the axial direction (+Y side). ) is provided.
  • the seal member 5S contacts and is aligned with the second step surface 66f.
  • the third inner peripheral surface 66c has the smallest diameter on the inner peripheral surface of the communication hole 65h.
  • the third inner circumferential surface 66c surrounds a connection space A, which will be described later, from the outside in the radial direction.
  • the fourth inner peripheral surface 66d surrounds the outer peripheral surface of the second bearing 5B.
  • the fourth inner peripheral surface 66d holds the second bearing 5B.
  • the diameter of the fourth inner peripheral surface 66d is larger than the diameter of the third inner peripheral surface 66c.
  • a third step surface 66g facing one side in the axial direction (-Y side) is provided between the fourth inner circumferential surface 66d and the third inner circumferential surface 66c.
  • the other end surface of the outer ring 5Ba of the second bearing 5B in the axial direction is pressed against the third step surface 66g.
  • the second bearing 5B supports the second shaft 44.
  • the end of the first shaft 21 on one axial side (-Y side) has a connection opening 21a.
  • the connecting opening 21a has a circular shape centered on the central axis J1 when viewed from the axial direction.
  • the connection opening 21a is connected to the hollow portion 21H of the first shaft 21.
  • the connection opening 21a has an inner circumferential surface facing radially inward.
  • a plurality of spline grooves 21s are provided on the inner peripheral surface of the connection opening 21a.
  • the plurality of spline grooves 21s extend in the axial direction.
  • the plurality of spline grooves 21s are arranged along the circumferential direction.
  • the end of the second shaft 44 on the other axial side (+Y side) has a connecting convex portion 44a.
  • the connecting convex portion 44a has a cylindrical shape centered on the central axis J1.
  • the connecting convex portion 44a has a distal end surface 44b facing the other side in the axial direction (+Y side) and an outer circumferential surface facing outward in the radial direction.
  • a plurality of spline protrusions 44s are provided on the outer peripheral surface of the connecting convex portion 44a.
  • the plurality of spline protrusions 44s extend in the axial direction.
  • the plurality of spline protrusions 44s are arranged along the circumferential direction.
  • FIG. 5 is a sectional view showing a connecting portion between the connecting opening 21a and the connecting convex portion 44a.
  • the first shaft 21 and the second shaft 44 are connected to each other by meshing with the spline groove 21s of the connection opening 21a and the spline protrusion 44s of the connection convex portion 44a.
  • the portion where the spline groove 21s and the spline protrusion 44s engage and are connected will be referred to as a connecting portion 3.
  • the spline groove 21s has a uniform cross-sectional shape and extends along the axial direction.
  • the spline protrusion 44s has a uniform cross-sectional shape and extends in the axial direction.
  • One spline projection 44s is inserted into one spline groove 21s.
  • the diameter of the bottom surface of the spline groove 21s facing radially inward is larger than the diameter of the tip surface facing radially outside of the spline protrusion 44s.
  • the width dimension of the spline groove 21s is larger than the width dimension of the spline protrusion 44s.
  • a gap 3a is provided between the inner surface of the spline groove 21s and the outer surface of the spline projection 44s.
  • the fluid O mutually moves between one end and the other end of the connecting portion 3 in the axial direction through the gap 3a.
  • the relative movement of the first shaft 21 and the second shaft 44 in the circumferential direction is restricted at the connecting portion 3. Therefore, the first shaft 21 and the second shaft 44 rotate synchronously around the central axis J1. Further, the first shaft 21 and the second shaft 44 allow relative movement in the axial direction in the connecting portion 3.
  • helical gears can be employed as the first gear 41 and the second gear 42. Therefore, the first gear 41 receives a reaction force directed in the axial direction from the second gear 42 during driving.
  • the axial force applied to the first gear 41 is It is possible to suppress the transmission of the heat to the first shaft 21 via the portion 3 . Therefore, it is possible to suppress a large thrust load from being applied to the bearings 5A, 5C that support the second shaft 44.
  • the end of the first shaft 21 on one axial side ( ⁇ Y side) has a stepped shape that becomes narrower toward the tip.
  • the first shaft 21 has a first outer peripheral surface 21d, a second outer peripheral surface 21e, and a third outer peripheral surface 21f.
  • the first outer circumferential surface 21d, the second outer circumferential surface 21e, and the third outer circumferential surface 21f are arranged in this order from the other axial side (+Y side) to the one side.
  • the diameters of the first outer circumferential surface 21d, the second outer circumferential surface 21e, and the third outer circumferential surface 21f decrease in this order.
  • the second outer peripheral surface 21e faces the first inner peripheral surface 66a of the communication hole 65h in the radial direction.
  • the first bearing 5A is mounted on the second outer peripheral surface 21e. That is, the second outer peripheral surface 21e is surrounded by the first bearing 5A.
  • a fourth step surface 21g facing one side in the axial direction (-Y side) is provided between the second outer peripheral surface 21e and the first outer peripheral surface 21d. One axial end surface of the inner ring 5Ac of the first bearing 5A is pressed against the fourth step surface 21g.
  • the third outer circumferential surface 21f is located at one end of the first shaft 21 in the axial direction (-Y side).
  • the third outer peripheral surface 21f faces the second inner peripheral surface 66b of the communication hole 65h in the radial direction.
  • the inner end of the seal member 5S contacts the third outer peripheral surface 21f. As the first shaft 21 rotates, the third outer peripheral surface 21f slides on the seal member 5S.
  • connection space A is provided between the first bearing 5A and the second bearing 5B in the axial direction in the communication hole 65h.
  • the space between the first bearing 5A and the second bearing 5B in the axial direction is divided into two by the seal member 5S. Specifically, it is divided into two spaces: a space sandwiched between the first bearing 5A and the seal member 5S in the axial direction, and a space sandwiched between the second bearing 5B and the seal member 5S in the axial direction.
  • the connection space A of this embodiment is a space sandwiched between the second bearing 5B and the seal member 5S in the axial direction. That is, in the connection space A, the connection opening 21a opens.
  • connection space A is sandwiched between the third inner peripheral surface 66c of the communication hole 65h and the outer peripheral surface of the second shaft 44 or the first shaft 21 in the radial direction, and between the second bearing 5B and the seal member 5S in the axial direction. It will be done. Fluid O is supplied to the connection space A from the gear chamber R2 via a first flow path 52a of a second supply flow path 52, which will be described later.
  • connection space A does not include the insides of the first shaft 21 and the second shaft 44.
  • the connection space A is a space radially inside the inner peripheral surface of the communication hole 65h and radially outside the outer peripheral surface of the first shaft 21 or the second shaft 44. That is, the connection space A is between the first bearing 5A and the second bearing 5B in the communication hole 65h in the axial direction, and between the inner peripheral surface of the communication hole 65h and the outer peripheral surface of the first shaft 21 or the second shaft 44. It is provided between the outer circumferential surface and the outer peripheral surface in the radial direction.
  • a seal member 5S is provided in the communication hole 65h of this embodiment.
  • the seal member 5S seals the gap between the inner peripheral surface of the communication hole 65h and the outer peripheral surface of the first shaft 21.
  • the fluid O that has flowed into the connection space A can be prevented from passing through the bearing 5A and flowing into the motor chamber R1. That is, the fluid O that has flowed into the connection space A can be easily guided to the connection part 3 and the hollow part 21H, and the motor 2 can be cooled suitably.
  • the seal member 5S retains the fluid O in the connection space A, a large amount of fluid O can be supplied to the second bearing 5B.
  • the seal member 5S is located between the first bearing 5A and the second bearing 5B. Moreover, in this embodiment, the connection space A is provided between the seal member 5S and the second bearing 5B.
  • the seal member 205S may be arranged on the other axial side (+Y side) of the first bearing 5A and the second bearing 5B.
  • the fluid O flowing into the connection space A can be supplied not only to the second bearing 5B but also to the first bearing 5A, thereby lubricating the first bearing 5A and the second bearing 5B.
  • the connection space A of this modification is sandwiched between the inner peripheral surface of the communication hole 65h and the outer peripheral surface of the second shaft 44 or the first shaft 21 in the radial direction, and is sandwiched between the first bearing 5A and the second shaft in the axial direction. This is the space sandwiched between the bearing 5B and the bearing 5B.
  • the seal member 5S is held on the inner peripheral surface of the communication hole 65h and contacts the outer peripheral surface of the first shaft 21. Further, in the first shaft 21, the outer diameter of the portion (third outer circumferential surface 21f) in contact with the seal member 5S is smaller than the outer diameter of the portion (second outer circumferential surface 21e) supported by the first bearing 5A. When the first shaft 21 rotates, the seal member 5S and the third outer peripheral surface 21f slide. By reducing the diameter of the third outer circumferential surface 21f, the sliding speed between the seal member 5S and the third outer circumferential surface 21f can be reduced, and heat generation due to sliding can be suppressed.
  • the diameter of the third outer circumferential surface 21f it is possible to reduce the torque applied to the first shaft 21 due to the dynamic friction force during sliding, thereby increasing the rotational efficiency of the first shaft 21. be able to.
  • the outer shape of the second outer circumferential surface 21e larger than the third outer circumferential surface 21f, a sufficient thickness of the first shaft 21 can be ensured inside the second outer circumferential surface 21e. Thereby, the rigidity of the portion of the first shaft 21 supported by the first bearing 5A can be increased, and the first shaft 21 can be stably held by the first bearing 5A.
  • the second supply channel 52 has a first channel 52a, a second channel 52e, and a third channel 52d.
  • the second supply flow path 52 reaches the motor chamber R1 from the gear chamber R2 through the connecting portion 3 in the first flow path 52a and the second flow path 52e.
  • the second supply flow path 52 of this embodiment further includes a third flow path 52d, which lubricates the second bearing 5B.
  • the first flow path 52a connects the gear chamber R2 and the connection space A.
  • the second flow path 52e connects the connection space A and the hollow portion (inside) 21H of the first shaft 21.
  • the third flow path 52d connects the connection space A and the gear chamber R2.
  • the first flow path 52a has a hole 84a, a first groove (groove) 11a, and a second groove 11b.
  • the hole 84a is provided in the partition wall 65a of the housing 6.
  • the hole 84a is formed by drilling.
  • the upper end of the hole 84 a is connected to the first storage section 84 .
  • the upper end of the hole 84a opens to the bottom surface of the first storage section 84.
  • the lower end of the hole 84a is connected to the inner circumferential surface of the cylindrical portion 11. That is, the hole portion 84a penetrates the cylindrical portion 11 in the radial direction. Further, the hole 84a extends from the first storage portion 84 to the inner circumferential surface of the cylindrical portion 11.
  • the hole portion 84a connects the first storage portion 84 and the inner peripheral surface of the cylindrical portion 11.
  • the cylindrical portion 11 is provided with a hole 84a that extends along the radial direction and constitutes a part of the first flow path 52a.
  • the hole 84a By forming a part of the first flow path 52a as the hole 84a, the fluid O can be stably supplied from the first storage section 84 to the connection space A.
  • the first flow path 52a may penetrate inside and outside of the cylindrical portion 11 by a notch provided in the cylindrical portion 11. That is, the cylindrical portion 11 may be provided with a notch that extends along the radial direction and constitutes a part of the first flow path 52a.
  • the first flow path 52a penetrates the inside of the partition wall 65a at the hole 84a.
  • the first flow path 52a may have a groove or a rib provided on the surface of the partition wall 65a instead of the hole 84a. That is, the partition wall 65a may have a groove or a rib that extends from the first storage section 84 toward the cylindrical section 11 and constitutes a part of the first flow path 52a.
  • the first groove 11a is provided on the inner circumferential surface of the cylindrical portion 11.
  • the first groove 11a of this embodiment is provided on the fourth inner peripheral surface 66d of the communication hole 65h.
  • the first groove 11a extends along the axial direction.
  • the first groove 11a is provided over the entire length of the fourth inner peripheral surface 66d in the axial direction.
  • the fourth inner peripheral surface 66d surrounds the second bearing 5B from the outside in the radial direction. Therefore, the first groove 11a is covered by the outer peripheral surface of the second bearing 5B. The fluid O that reaches the first groove 11a flows through a space surrounded by the inner surface of the first groove 11a and the outer peripheral surface of the second bearing 5B.
  • the first groove 11a has a bottom surface 11c facing radially inward.
  • a hole 84a is opened in the bottom surface 11c. That is, the hole 84a opens to the bottom surface 11c of the first groove 11a.
  • the opening of the hole 84a is covered by the outer peripheral surface of the second bearing 5B, and the fluid O is not supplied from the hole 84a to the connection space A. It's not done smoothly.
  • the first groove 11a is provided in the fourth inner circumferential surface 66d, and the hole 84a is opened at the bottom surface 11c of the first groove 11a, thereby allowing fluid O to flow smoothly from the opening of the hole 84a. can be supplied to
  • the second groove 11b is provided on the third step surface 66g, which is the inner peripheral surface of the communication hole 65h.
  • the second groove 11b extends in the radial direction.
  • the radially outer end of the second groove 11b is connected to the end of the first groove 11a on the other axial side (+Y side).
  • a radially inner end of the second groove 11b is connected to the connection space A.
  • the third step surface 66g contacts the outer ring 5Ba of the second bearing 5B. Therefore, the second groove 11b is covered by the outer ring 5Ba of the second bearing 5B. The fluid O reaching the second groove 11b flows through a space surrounded by the inner surface of the second groove 11b and the outer ring 5Ba of the second bearing 5B.
  • the second channel 52e has an inflow channel 52b and an outflow channel 52c.
  • Both the inflow channel 52b and the outflow channel 52c are channels that connect the connection space A and the hollow portion 21H of the first shaft 21.
  • the inflow channel 52b is a path through which the fluid O flows from the connection space A toward the hollow portion 21H.
  • the outflow channel 52c is a path through which the fluid O flows from the hollow portion 21H toward the connection space A.
  • Both the inflow channel 52b and the outflow channel 52c pass between the spline groove 21s and the spline protrusion 44s.
  • the second supply flow path 52 may include a first flow path 252a of a modified example. Similar to the embodiment described above, the first flow path 252a of the modified example connects the connection space A and the gear chamber R2.
  • the first flow path 252a of the modified example is a flow path provided between the inner ring 5Bc and the outer ring 5Ba of the second bearing 5B. That is, the first flow path 252a is a flow path that includes the second bearing 5B.
  • the second bearing 5B can be lubricated by the fluid O flowing through the first flow path 252a.
  • the fluid O can flow through the inflow channel 52b and the outflow channel 52c simultaneously.
  • the amount of fluid O accumulated in the connection space A is relatively large and the amount of fluid O remaining in the hollow portion 21H is relatively small, more fluid O flows into the inflow channel 52b.
  • the amount of fluid O accumulated in the connection space A is relatively small and the amount of fluid O remaining in the hollow portion 21H is relatively large, more fluid O flows through the outflow channel 52c.
  • the fluid O can be supplied to the connecting portion 3 by flowing through the second flow path 52e.
  • the fluid O can be filled between the spline groove 21s and the spline protrusion 44s, and the impact on the connecting portion 3 when the rotation direction of the first shaft 21 is switched can be alleviated.
  • the first shaft 21 is arranged in the motor chamber R1. That is, the hollow portion 21H inside the first shaft 21 is a part of the motor chamber R1.
  • the second flow path 52e connects the connection space A and the motor chamber R1. Therefore, the fluid O in the gear chamber R2 can be moved to the motor chamber R1 via the connection space A, and the fluid O can be used for cooling the motor 2 and lubricating the third bearing 5C.
  • the first flow path 52a and the second flow path 52e of this embodiment are connected in the connection space A. Therefore, the second supply flow path 52 is provided so as to pass through the connection space A at the connection portion between the first flow path 52a and the second flow path 52e.
  • a connection opening 21a opens in the connection space A.
  • the fluid O in this connection space A is supplied to the connection part 3.
  • the first flow path 52a and the second flow path 52e supply the fluid O between the motor chamber R1 and the gear chamber R2. can be moved.
  • the structure of the second supply flow path 52 is simplified compared to the case where a flow path for supplying the fluid O to the connecting portion 3 and a flow path connecting the motor chamber R1 and the gear chamber R2 are provided separately. It is possible. As a result, the housing 6 in which the second supply channel 52 is provided can be downsized.
  • the first flow path 52a supplies fluid O from the gear chamber R2 to the connection space A
  • the second flow path 52e supplies fluid O from the connection space A to the motor chamber R1. do. Therefore, the fluid O in the gear chamber R2 can be sent to the motor chamber R1 while lubricating the connecting portion 3.
  • connection opening 21a is connected to the hollow portion 21H of the first shaft 21. Therefore, when the supply of fluid O from the first storage section 84 to the connection section 3 is delayed, the fluid O in the hollow section 21H flows through the outflow channel 52c and reaches the connection space A. That is, the fluid O remaining in the hollow portion 21H can gradually travel through the gap between the spline groove 21s and the spline protrusion 44s, thereby lubricating the connecting portion 3.
  • the second shaft 44 of this embodiment is a solid shaft. Therefore, the fluid O accumulated in the hollow portion 21H of the first shaft 21 does not flow into the inside of the second shaft 44. According to this embodiment, the fluid O accumulated in the hollow part 21H can be easily guided to the other axial side of the hollow part 21H, and the motor 2 can be cooled and the third bearing 5C can be suitably lubricated.
  • the third flow path 52d is a flow path provided between the inner ring 5Bc and outer ring 5Ba of the second bearing 5B. That is, the third flow path 52d is a flow path that includes the second bearing 5B. According to this embodiment, the second bearing 5B is lubricated by the fluid O flowing through the third flow path 52d.
  • connection space A of this embodiment is connected to the first storage section 84 via the first flow path 52a.
  • the fluid O is stably supplied to the connection space A from the first storage section 84.
  • the connection space A can stably supply the fluid O to the second flow path 52e and the third flow path 52d, and lubricate the connection portion 3 in the second flow path 52e.
  • the second bearing 5B can be lubricated in the third flow path 52d.
  • the second bearing 5B of this embodiment supports the second shaft 44 of the power transmission section 4. Therefore, vibrations caused by the meshing of the gears are more easily transmitted to the second bearing 5B than to the first bearing 5A. According to this embodiment, the operation of the second bearing 5B can be stabilized by providing the third flow path 52d between the outer ring 5Ba and the inner ring 5Bc of the second bearing 5B to lubricate the second bearing 5B. can.
  • the first bearing 5A and the second bearing 5B are ball bearings.
  • the first bearing 5A and the second bearing 5B have spherical rolling elements 5Ab and 5Bb, respectively.
  • the diameter of the rolling elements 5Bb of the second bearing 5B is larger than the diameter of the rolling elements 5Ab of the first bearing 5A.
  • the strength and rigidity of the second bearing 5B which is susceptible to vibrations from the power transmission section 4, can be increased, and the operation of the power transmission section 4 can be made smooth.
  • helical gears are used as the first gear 41 and the second gear 42, an axial force is applied to the second bearing 5B when the power transmission section 4 is driven.
  • the second bearing 5B can stably support the second shaft 44 against the axial force applied to the second shaft 44 by increasing the size of the rolling elements 5Bb.
  • first bearing 5A and the second bearing 5B may be roller bearings having cylindrical rolling elements 5Ab and 5Bb. Even in this case, the above-mentioned effect can be obtained if the diameters of the spherical or cylindrical rolling elements 5Ab and 5Bb are compared and the first bearing 5A is larger.
  • the connecting opening 21a is provided on the first shaft 21, and the connecting convex portion 44a is provided on the second shaft 44. Since the connecting protrusion 44a and the connecting opening 21a fit into each other, the shaft provided with the connecting protrusion 44a has a larger diameter than the shaft provided with the recess. According to this embodiment, the second shaft 44 can be made smaller in diameter than the first shaft 21 by providing the first shaft 21 with the connecting opening 21a and the second shaft 44 with the connecting convex portion 44a. Therefore, even if the rolling elements 5Bb of the second bearing 5B that supports the second shaft 44 are increased in size, the outer diameter of the second bearing 5B can be prevented from becoming too large.
  • the second bearing 5B is supported adjacent to the fifth bearing 5E (see FIG.
  • the second shaft 44 and the third shaft 45 can be disposed close to each other by preventing the outer diameter of the second bearing 5B from becoming too large. Thereby, it is possible to suppress the housing 6 from increasing in size.
  • FIG. 7 is a sectional view showing the connecting portion 3 of the drive device 101 of the second embodiment. Note that the same reference numerals are given to the same components as in the above-described embodiment, and the explanation thereof will be omitted.
  • the drive device 101 of this embodiment includes a motor 2 having a first shaft 121 (omitted in FIG. 7), a power transmission section 4 having a second shaft 44 (omitted in FIG. 7), and a housing. 106, a first bearing 5A, a second bearing 5B, and a second supply channel 152.
  • the housing 106 has a partition wall 65a that partitions the motor chamber R1 and the gear chamber R2. Further, the partition wall 65a is provided with a communication hole 65h that communicates the motor chamber R1 and the gear chamber R2.
  • the partition wall 65a has a cylindrical portion 111 that protrudes toward the gear chamber R2 (ie, one axial side (-Y side)) along the inner edge of the communication hole 65h.
  • the inner peripheral surface of the communication hole 65h holds the first bearing 5A, the second bearing 5B, and the seal member 105S.
  • the first shaft 121 and the second shaft 44 of this embodiment are both solid shafts.
  • the first shaft 121 has a connecting opening 121a at one axial end (-Y side).
  • the connection opening 121a of this embodiment has a concave shape.
  • a plurality of spline grooves 21s are provided on the inner peripheral surface of the connection opening 121a.
  • the connecting convex portion 44a of the second shaft 44 is inserted into the connecting opening 121a.
  • the spline groove 21s of the connection opening 121a and the spline protrusion 44s of the connection convex part 44a fit together to form the connection part 3.
  • an axial gap is provided between the bottom surface 121b of the connection opening 121a and the tip surface 44b of the connection convex portion 44a.
  • the gap between the bottom surface 121b and the tip surface 44b will be referred to as a third storage section B. That is, the third reservoir B is provided between the bottom surface 121b and the tip surface 44b.
  • the third storage portion B is a space surrounded from the outside in the radial direction by the inner circumferential surface of the connection opening 121a, and sandwiched in the axial direction by the bottom surface 121b and the tip surface 44b.
  • the fluid O remains in the third reservoir B.
  • a connection space A is provided between the first bearing 5A and the second bearing 5B in the axial direction in the communication hole 65h.
  • a connection opening 121a opens in the connection space A.
  • a seal member 105S is provided in the communication hole 65h.
  • the cylindrical portion 111 of this embodiment further extends to one side (-Y side) in the axial direction with respect to the second bearing 5B.
  • the seal member 105S is fixed to the inner peripheral surface of the cylindrical portion 111 on one axial side (-Y side) of the second bearing 5B. That is, the seal member 105S is arranged on one side in the axial direction (-Y side) of the first bearing 5A and the second bearing 5B.
  • the fluid O that has flowed into the connection space A can be supplied to the first bearing 5A and the second bearing 5B, and the first bearing 5A and the second bearing 5B can be suitably lubricated. Furthermore, the seal member 105S can suppress the fluid O flowing into the connection space A from flowing out to the gear chamber R2 side. Since the seal member 105S retains the fluid O in the connection space A, a large amount of the fluid O can be supplied to the connection portion 3, the first bearing 5A, and the second bearing 5B.
  • the second supply channel (channel) 152 has a first channel 52a, a second channel 152b, an inflow channel 152c, and an outflow channel 152d.
  • the first flow path 52a connects the gear chamber R2 and the connection space A.
  • the second flow path 152b connects the connection space A and the motor chamber R1.
  • Both the inflow channel 152c and the outflow channel 152d are channels that connect the connection space A and the third storage section B.
  • the first flow path 52a has the same configuration as the first embodiment.
  • the second flow path 152b is a flow path provided between the inner ring 5Ac and outer ring 5Aa of the first bearing 5A. That is, the second flow path 152b is a flow path that includes the first bearing 5A. According to this embodiment, the first bearing 5A is lubricated by the fluid O flowing through the second flow path 152b.
  • the inflow channel 152c is a path through which the fluid O flows from the connection space A toward the third storage section B.
  • the outflow channel 152d is a path through which the fluid O flows from the third storage section B toward the connection space A. Both the inflow channel 152c and the outflow channel 152d pass between the spline groove 21s and the spline protrusion 44s.
  • the first flow path 52a and the second flow path 152b are connected in the connection space A. That is, the second supply flow path 152 is provided so as to pass through the connection space A at the connection portion between the first flow path 52a and the second flow path 152b. Therefore, while supplying the fluid O from the connection space A to the connection part 3, the fluid O can be moved between the motor chamber R1 and the gear chamber R2 through the first flow path 52a and the second flow path 152b.
  • an inflow channel 152c and an outflow channel 152d are interposed between the first channel 52a and the second channel 152b.
  • the connection space A is an annular space extending in the circumferential direction centering on the central axis J1, and the first flow path 52a and the second flow path 152b are directly connected.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Power Engineering (AREA)
  • General Details Of Gearings (AREA)

Abstract

One aspect of a drive device according to the present invention comprises a motor, a power transmission part, a housing, first and second bearings, and a flow path in which a fluid flows. An end part on one side in the axial direction of a first shaft of the motor has a connection opening in which a spline groove is provided. An end part on the other side in the axial direction of a second shaft of the power transmission part has a connection protrusion in which a spline projection is provided. The first shaft and the second shaft are connected by the spline groove and the spline projection meshing with each other. Provided to a partition wall of the housing is a communicating hole via which a motor chamber and a gear chamber are in communication. The inner peripheral surface of the communicating hole holds the first bearing and the second bearing. Between the axial direction of the second bearing and the first bearing in the communicating hole is provided a connection space into which the connection opening opens. The flow path has a first flow path that connects the gear chamber and the connection space and a second flow path that connects the connection space and the motor chamber.

Description

駆動装置drive device
　本発明は、駆動装置に関する。
　本願は、２０２２年３月３１日に日本に出願された特願２０２２－０６１１３６号に基づき優先権を主張し、その内容をここに援用する。 The present invention relates to a drive device.
This application claims priority based on Japanese Patent Application No. 2022-061136 filed in Japan on March 31, 2022, the contents of which are incorporated herein.
　近年、電気自動車に搭載される駆動装置として、モータと減速装置とをユニット化した駆動装置の開発が進んでいる。このような駆動装置では、モータ側のシャフトと減速装置のシャフトとがスプライン嵌合などの連結構造を介して互いに連結される。特許文献１には、モータ側および減速装置側のシャフトを中空シャフトとして、中空シャフト内にオイルを流すことで連結部にオイルを供給する構造が開示されている。 In recent years, the development of a drive device that combines a motor and a speed reduction device into a unit has been progressing as a drive device installed in an electric vehicle. In such a drive device, the shaft on the motor side and the shaft of the reduction gear are connected to each other via a connection structure such as spline fitting. Patent Document 1 discloses a structure in which the shafts on the motor side and the speed reducer side are hollow shafts, and oil is supplied to the connecting portion by flowing oil into the hollow shafts.
特開２０１７－７５６２７号公報JP2017-75627A
　潤滑に用いる流体をモータの冷却にも用いる場合がある。この場合、流体をギヤ室からモータ室に送る必要があるが、連結部潤滑用の流路とは別に、新たな流路を設ける場合、流路の構造が複雑化する問題がある。 The fluid used for lubrication may also be used to cool the motor. In this case, it is necessary to send fluid from the gear chamber to the motor chamber, but if a new flow path is provided in addition to the flow path for lubricating the connecting portion, there is a problem in that the structure of the flow path becomes complicated.
　本発明は、上記事情に鑑みて、シャフトの連結部に流体を供給しつつモータ室とギヤ室との間で流体を移動させることができる駆動装置の提供を目的の一つとする。 In view of the above circumstances, one object of the present invention is to provide a drive device that can move fluid between a motor chamber and a gear chamber while supplying fluid to a connecting portion of a shaft.
　本発明の駆動装置の一つの態様は、中心軸線を中心として回転する第１シャフトを有するロータ、および前記ロータを囲むステータを有するモータと、複数のギヤ、および前記中心軸線を中心として回転する第２シャフトを有し、前記モータの動力を伝達する動力伝達部と、前記モータを収容するモータ室と前記動力伝達部を収容するギヤ室とが内部に設けられるハウジングと、前記第１シャフトを支持する第１ベアリングと、前記第２シャフトを支持する第２ベアリングと、流体が流れる流路と、を備える。前記第１シャフトの軸方向一方側の端部は、内周面に軸方向に延びる複数のスプライン溝が設けられる連結開口部を有する。前記第２シャフトの軸方向他方側の端部は、外周面に軸方向に延びる複数のスプライン突起が設けられる連結凸部を有する。前記第１シャフトと前記第２シャフトとは、前記連結開口部の前記スプライン溝と前記連結凸部の前記スプライン突起との噛み合いにより互いに連結される。前記ハウジングは、前記モータ室と前記ギヤ室とを区画する隔壁を有する。前記隔壁には、前記モータ室と前記ギヤ室とを連通する連通孔が設けられる。前記連通孔の内周面は、前記第１ベアリングおよび前記第２ベアリングを保持する。前記連通孔における前記第１ベアリングと前記第２ベアリングの軸方向の間には、前記連結開口部が開口する連結空間が設けられる。前記流路は、前記ギヤ室と前記連結空間とを繋ぐ第１流路と、前記連結空間と前記モータ室とを繋ぐ第２流路と、を有する。 One aspect of the drive device of the present invention includes a rotor having a first shaft that rotates around a central axis, a motor having a stator surrounding the rotor, a plurality of gears, and a first shaft that rotates around the central axis. a housing that has two shafts and is provided with a power transmission section that transmits the power of the motor, a motor chamber that accommodates the motor, and a gear chamber that accommodates the power transmission section; and a housing that supports the first shaft. A first bearing that supports the second shaft, a second bearing that supports the second shaft, and a flow path through which fluid flows. One end of the first shaft in the axial direction has a connecting opening in which a plurality of spline grooves extending in the axial direction are provided on the inner circumferential surface. The other end of the second shaft in the axial direction has a connecting convex portion provided with a plurality of spline protrusions extending in the axial direction on the outer peripheral surface. The first shaft and the second shaft are connected to each other by engagement between the spline groove of the connection opening and the spline protrusion of the connection convex portion. The housing has a partition wall that partitions the motor chamber and the gear chamber. The partition wall is provided with a communication hole that communicates the motor chamber and the gear chamber. The inner peripheral surface of the communication hole holds the first bearing and the second bearing. A connection space in which the connection opening opens is provided between the first bearing and the second bearing in the communication hole in the axial direction. The flow path includes a first flow path that connects the gear chamber and the connection space, and a second flow path that connects the connection space and the motor chamber.
　本発明の一つの態様によれば、シャフトの連結部に流体を供給しつつモータ室とギヤ室との間で流体を移動させることができる駆動装置を提供できる。 According to one aspect of the present invention, it is possible to provide a drive device that can move fluid between a motor chamber and a gear chamber while supplying fluid to a connecting portion of a shaft.
図１は、一実施形態の駆動装置の概念図である。FIG. 1 is a conceptual diagram of a drive device according to an embodiment. 図２は、一実施形態のギヤ室を軸方向一方側から見た正面図である。FIG. 2 is a front view of the gear chamber of one embodiment viewed from one side in the axial direction. 図３は、一実施形態のギヤ室を軸方向他方側から見た背面図である。FIG. 3 is a rear view of the gear chamber of one embodiment viewed from the other axial side. 図４は、一実施形態の第１シャフトおよび第２シャフトの連結部の断面図である。FIG. 4 is a cross-sectional view of a connecting portion of a first shaft and a second shaft in one embodiment. 図５は、一実施形態の連結部の部分断面図である。FIG. 5 is a partial cross-sectional view of a coupling portion of one embodiment. 図６は、変形例の第１シャフトおよび第２シャフトの連結部の断面図である。FIG. 6 is a cross-sectional view of a connecting portion of a first shaft and a second shaft in a modified example. 図７は、第２実施形態の第１シャフトおよび第２シャフトの連結部を示す断面図である。FIG. 7 is a sectional view showing a connecting portion between the first shaft and the second shaft of the second embodiment.
　以下の説明では、駆動装置１が水平な路面上に位置する車両に搭載された場合の位置関係を基に、重力方向を規定して説明する。また、図面においては、適宜３次元直交座標系としてＸＹＺ座標系を示す。 In the following explanation, the direction of gravity will be defined and explained based on the positional relationship when the drive device 1 is mounted on a vehicle located on a horizontal road surface. In addition, in the drawings, an XYZ coordinate system is appropriately shown as a three-dimensional orthogonal coordinate system.
　ＸＹＺ座標系において、Ｚ軸方向は、鉛直方向（すなわち上下方向）を示し、＋Ｚ方向が上側（重力方向の反対側）であり、－Ｚ方向が下側（重力方向）である。また、Ｘ軸方向は、Ｚ軸方向と直交する方向であって駆動装置１が搭載される車両の前後方向を示す。以下の実施形態において、Ｘ軸の矢印が向く側（＋Ｘ側）は、車両における前側であり、Ｘ軸の矢印が向く側と逆側（－Ｘ側）は、車両における後側である。Ｙ軸方向は、Ｘ軸方向とＺ軸方向との両方と直交する方向であって、車両の幅方向（左右方向）を示す。以下の実施形態において、Ｙ軸の矢印が向く側（＋Ｙ側）は、車両における左側であり、Ｙ軸の矢印が向く側と逆側（－Ｙ側）は、車両における右側である。前後方向および左右方向は、鉛直方向と直交する水平方向である。 In the XYZ coordinate system, the Z-axis direction indicates the vertical direction (that is, the up-down direction), the +Z direction is the upper side (opposite to the direction of gravity), and the -Z direction is the lower side (the direction of gravity). Moreover, the X-axis direction is a direction orthogonal to the Z-axis direction, and indicates the front-rear direction of the vehicle in which the drive device 1 is mounted. In the following embodiments, the side to which the X-axis arrow points (+X side) is the front side of the vehicle, and the side opposite to the side to which the X-axis arrow points (-X side) is the rear side of the vehicle. The Y-axis direction is a direction perpendicular to both the X-axis direction and the Z-axis direction, and indicates the width direction (left-right direction) of the vehicle. In the following embodiments, the side to which the Y-axis arrow points (+Y side) is the left side of the vehicle, and the side opposite to the side to which the Y-axis arrow points (-Y side) is the right side of the vehicle. The front-rear direction and the left-right direction are horizontal directions perpendicular to the vertical direction.
　以下の説明において特に断りのない限り、モータ２の中心軸線Ｊ１に平行な方向（Ｙ軸方向）を単に「軸方向」と呼び、中心軸線Ｊ１を中心とする径方向を単に「径方向」と呼び、中心軸線Ｊ１を中心とする周方向、すなわち、中心軸線Ｊ１の軸周りを単に「周方向」と呼ぶ。ただし、上記の「平行な方向」は、略平行な方向も含む。さらに、以下の説明において、中心軸線Ｊ１の軸方向のうち、－Ｙ方向を単に軸方向一方側と呼び、＋Ｙ方向を単に軸方向他方側と呼ぶ場合がある。 In the following description, unless otherwise specified, the direction parallel to the central axis J1 of the motor 2 (Y-axis direction) is simply referred to as the "axial direction", and the radial direction centered on the central axis J1 is simply referred to as the "radial direction". The circumferential direction centered on the central axis J1, that is, the circumferential direction around the central axis J1 is simply referred to as the "circumferential direction." However, the above-mentioned "parallel direction" also includes substantially parallel directions. Furthermore, in the following description, among the axial directions of the central axis J1, the -Y direction may be simply referred to as one axial direction, and the +Y direction may simply be referred to as the other axial direction.
　（第１実施形態）
　＜駆動装置＞
　図１は、第１実施形態の駆動装置１の概念図である。
　本実施形態の駆動装置１は、ハイブリッド自動車（ＨＥＶ）、プラグインハイブリッド自動車（ＰＨＶ）、電気自動車（ＥＶ）等、モータを動力源とする車両に搭載され、その動力源として使用される。 (First embodiment)
<Drive device>
FIG. 1 is a conceptual diagram of a drive device 1 according to the first embodiment.
The drive device 1 of this embodiment is mounted on a vehicle that uses a motor as a power source, such as a hybrid vehicle (HEV), a plug-in hybrid vehicle (PHV), or an electric vehicle (EV), and is used as the power source.
　図１に示すように、駆動装置１は、モータ２と動力伝達部４とハウジング６と複数のベアリング５Ａ、５Ｂ、５Ｃ、５Ｄ、５Ｅ、５Ｆ、５Ｇ、５Ｈとを備える。ハウジング６は、モータ２、動力伝達部４、および複数のベアリング５Ａ～５Ｈを収容する。以下の説明において、複数のベアリング５Ａ～５Ｈを、それぞれ第１ベアリング５Ａ、第２ベアリング５Ｂ、第３ベアリング５Ｃ、第４ベアリング５Ｄ、第５ベアリング５Ｅ、第６ベアリング５Ｆ、第７ベアリング５Ｇ、および第８ベアリング５Ｈと、呼ぶ場合がある。 As shown in FIG. 1, the drive device 1 includes a motor 2, a power transmission section 4, a housing 6, and a plurality of bearings 5A, 5B, 5C, 5D, 5E, 5F, 5G, and 5H. Housing 6 accommodates motor 2, power transmission section 4, and a plurality of bearings 5A to 5H. In the following description, the plurality of bearings 5A to 5H are respectively referred to as a first bearing 5A, a second bearing 5B, a third bearing 5C, a fourth bearing 5D, a fifth bearing 5E, a sixth bearing 5F, a seventh bearing 5G, and It may be called the eighth bearing 5H.
　＜モータ＞
　本実施形態のモータ２は、インナーロータ型の三相交流モータである。なお、モータ２の構成は本実施形態に限定されず、例えば四相以上の交流モータであってもよい。 <Motor>
The motor 2 of this embodiment is an inner rotor type three-phase AC motor. Note that the configuration of the motor 2 is not limited to this embodiment, and may be, for example, a four-phase or more AC motor.
　モータ２は、ハウジング６のモータ室Ｒ１に配置される。モータ２は、ロータ２０と、ロータ２０と径方向に対向するステータ３０と、を備える。本実施形態のモータ２は、ステータ３０の内側にロータ２０が配置されるインナーロータ型モータである。 The motor 2 is arranged in the motor chamber R1 of the housing 6. The motor 2 includes a rotor 20 and a stator 30 that faces the rotor 20 in the radial direction. The motor 2 of this embodiment is an inner rotor type motor in which a rotor 20 is arranged inside a stator 30.
　ロータ２０は、水平方向に延びる中心軸線Ｊ１を中心として回転する。ロータ２０は、第１シャフト２１と、第１シャフト２１の外周面に固定されるロータコア２４と、ロータコア２４に固定されるロータマグネット（図示略）と、を有する。ロータ２０のトルクは、動力伝達部４に伝達される。第１シャフト２１は、中心軸線Ｊ１を中心として軸方向に沿って延びる。第１シャフト２１は、中心軸線Ｊ１を中心として回転する。第１シャフト２１の両端部は、第１ベアリング５Ａ、および第３ベアリング５Ｃに回転可能に支持される。 The rotor 20 rotates around a central axis J1 that extends in the horizontal direction. The rotor 20 includes a first shaft 21, a rotor core 24 fixed to the outer peripheral surface of the first shaft 21, and a rotor magnet (not shown) fixed to the rotor core 24. The torque of the rotor 20 is transmitted to the power transmission section 4. The first shaft 21 extends in the axial direction centering on the central axis J1. The first shaft 21 rotates around the central axis J1. Both ends of the first shaft 21 are rotatably supported by a first bearing 5A and a third bearing 5C.
　第１シャフト２１は、筒状の中空シャフトである。以下の説明において、第１シャフト２１の内部を中空部２１Ｈと呼ぶ。第１シャフト２１の中空部２１Ｈは、軸方向一方側（－Ｙ側）および軸方向他方側（＋Ｙ側）に開口する。 The first shaft 21 is a cylindrical hollow shaft. In the following description, the inside of the first shaft 21 will be referred to as a hollow portion 21H. The hollow portion 21H of the first shaft 21 opens on one axial side (-Y side) and the other axial side (+Y side).
　第１シャフト２１には、径方向に貫通する貫通孔２１ｈが設けられる。貫通孔２１ｈは、周方向に間隔を空けて複数設けられている。また、ロータコア２４には、貫通孔２１ｈに繋がるロータ内流路２４Ｈが設けられる。 The first shaft 21 is provided with a through hole 21h that penetrates in the radial direction. A plurality of through holes 21h are provided at intervals in the circumferential direction. Further, the rotor core 24 is provided with an internal rotor flow path 24H that is connected to the through hole 21h.
　後述するように、中空部２１Ｈには、軸方向一方側（－Ｙ側）の開口から流体Ｏが流入する。中空部２１Ｈの流体Ｏは、ロータ２０の回転に伴う遠心力によって、貫通孔２１ｈおよびロータ内流路２４Ｈを通過しステータ３０に飛散する。流体Ｏは、ロータ２０およびステータ３０を冷却する。また、中空部２１Ｈの流体Ｏは、軸方向他方側（＋Ｙ側）から漏出し第３ベアリング５Ｃを潤滑する。 As will be described later, fluid O flows into the hollow portion 21H from an opening on one side in the axial direction (−Y side). The fluid O in the hollow portion 21H passes through the through hole 21h and the rotor internal flow path 24H and scatters onto the stator 30 due to the centrifugal force caused by the rotation of the rotor 20. Fluid O cools rotor 20 and stator 30. Further, the fluid O in the hollow portion 21H leaks from the other axial side (+Y side) and lubricates the third bearing 5C.
　ステータ３０は、ハウジング６に保持される。ステータ３０は、ロータ２０を径方向外側から囲む。ステータ３０は、中心軸線Ｊ１を中心とする環状のステータコア３２と、ステータコア３２に装着されるコイル３１と、ステータコア３２とコイル３１との間に介在するインシュレータ（図示略）とを有する。ステータコア３２は、環状のヨークの内周面から径方向内方に複数の磁極歯（図示略）を有する。磁極歯の間には、コイル線が配置される。隣り合う磁極歯の間の間隙内に位置するコイル線は、コイル３１を構成する。インシュレータは、絶縁性の材料からなる。 The stator 30 is held in the housing 6. The stator 30 surrounds the rotor 20 from the outside in the radial direction. The stator 30 includes an annular stator core 32 centered on the central axis J1, a coil 31 attached to the stator core 32, and an insulator (not shown) interposed between the stator core 32 and the coil 31. The stator core 32 has a plurality of magnetic pole teeth (not shown) radially inward from the inner peripheral surface of the annular yoke. A coil wire is arranged between the magnetic pole teeth. The coil wire located within the gap between adjacent magnetic pole teeth constitutes the coil 31. The insulator is made of an insulating material.
　＜動力伝達部＞
　動力伝達部４は、モータ２に対し軸方向一方側（－Ｙ側）に配置される。動力伝達部４は、ロータ２０に接続されてモータ２の動力を伝達し出力シャフト４７に出力する。動力伝達部４は、減速装置４ａと差動装置４ｂとを有する。すなわち、駆動装置１は、減速装置４ａおよび差動装置４ｂを有する。 <Power transmission section>
The power transmission section 4 is arranged on one axial side (-Y side) with respect to the motor 2. The power transmission section 4 is connected to the rotor 20 and transmits the power of the motor 2, and outputs the power to the output shaft 47. The power transmission section 4 includes a reduction gear 4a and a differential gear 4b. That is, the drive device 1 includes a speed reduction device 4a and a differential device 4b.
　モータ２から出力されるトルクは、減速装置４ａを介して差動装置４ｂに伝達される。本実施形態の減速装置４ａでは、各ギヤの回転軸線が平行に配置される差動装置４ｂは、車両の旋回時に、左右の車輪の速度差を吸収しつつ左右両輪に同トルクを伝達する。 The torque output from the motor 2 is transmitted to the differential gear 4b via the reduction gear 4a. In the speed reduction device 4a of this embodiment, the differential device 4b, in which the rotational axes of the respective gears are arranged in parallel, transmits the same torque to both the left and right wheels while absorbing the speed difference between the left and right wheels when the vehicle turns.
　減速装置４ａは、第２シャフト４４、第３シャフト４５、第１ギヤ４１、第２ギヤ４２、および第３ギヤ４３を有する。差動装置４ｂは、リングギヤ４６ｇ、デフケース４６、およびデフケース４６の内部に配置される差動機構部４６ｃを有する。すなわち、動力伝達部４は、複数のギヤ４１、４２、４３、４６ｇと、複数のシャフト４４、４５と、を有する。 The reduction gear 4a has a second shaft 44, a third shaft 45, a first gear 41, a second gear 42, and a third gear 43. The differential device 4b includes a ring gear 46g, a differential case 46, and a differential mechanism section 46c disposed inside the differential case 46. That is, the power transmission section 4 includes a plurality of gears 41, 42, 43, 46g and a plurality of shafts 44, 45.
　第２シャフト４４は、中心軸線Ｊ１を中心として軸方向に延びる。第２シャフト４４は、第１シャフト２１と同軸上に配置される。第２シャフト４４は、軸方向他方側（＋Ｙ側）の端部において、第１シャフト２１の軸方向一方側（－Ｙ側）の端部に連結される。第２シャフト４４は、第１シャフト２１ととともに中心軸線Ｊ１を中心として回転する。第２シャフト４４は、第２ベアリング５Ｂ、および第４ベアリング５Ｄに回転可能に支持される。 The second shaft 44 extends in the axial direction centering on the central axis J1. The second shaft 44 is arranged coaxially with the first shaft 21. The second shaft 44 is connected to the end of the first shaft 21 on the one axial side (-Y side) at the end on the other axial side (+Y side). The second shaft 44 rotates together with the first shaft 21 about the central axis J1. The second shaft 44 is rotatably supported by the second bearing 5B and the fourth bearing 5D.
　第１ギヤ４１は、第２シャフト４４の外周面に設けられる。第１ギヤ４１は、第２シャフト４４とともに中心軸線Ｊ１周りに回転する。 The first gear 41 is provided on the outer peripheral surface of the second shaft 44. The first gear 41 rotates together with the second shaft 44 around the central axis J1.
　第３シャフト４５は、中心軸線Ｊ１と平行な中間軸線Ｊ２を中心として回転する。第３シャフト４５は、第５ベアリング５Ｅ、および第６ベアリング５Ｆに回転可能に支持される。 The third shaft 45 rotates around an intermediate axis J2 that is parallel to the central axis J1. The third shaft 45 is rotatably supported by the fifth bearing 5E and the sixth bearing 5F.
　第２ギヤ４２と第３ギヤ４３とは、軸方向に並んで配置される。第２ギヤ４２および第３ギヤ４３は、第３シャフト４５の外周面に設けられる。第２ギヤ４２および第３ギヤ４３は、第３シャフト４５を介して接続される。第２ギヤ４２および第３ギヤ４３は、中間軸線Ｊ２を中心として回転する。第２ギヤ４２は、第１ギヤ４１と噛み合う。第３ギヤ４３は、差動装置４ｂのリングギヤ４６ｇと噛み合う。本実施形態において、第１ギヤ４１、第２ギヤ４２、第３ギヤ４３、およびリングギヤ４６ｇは、それぞれヘリカルギヤである。 The second gear 42 and the third gear 43 are arranged side by side in the axial direction. The second gear 42 and the third gear 43 are provided on the outer peripheral surface of the third shaft 45. The second gear 42 and the third gear 43 are connected via a third shaft 45. The second gear 42 and the third gear 43 rotate about the intermediate axis J2. The second gear 42 meshes with the first gear 41. The third gear 43 meshes with a ring gear 46g of the differential device 4b. In this embodiment, the first gear 41, the second gear 42, the third gear 43, and the ring gear 46g are each helical gears.
　リングギヤ４６ｇは、中心軸線Ｊ１と平行な出力軸線Ｊ３を中心として回転する。リングギヤ４６ｇには、モータ２から出力されるトルクが減速装置４ａを介して伝えられる。リングギヤ４６ｇは、デフケース４６に固定される。 The ring gear 46g rotates around an output axis J3 that is parallel to the central axis J1. Torque output from the motor 2 is transmitted to the ring gear 46g via the reduction gear 4a. Ring gear 46g is fixed to differential case 46.
　デフケース４６は、内部に差動機構部４６ｃを収容するケース部４６ｂと、ケース部４６ｂに対して軸方向他方側および他方側にそれぞれ突出するデフケースシャフト４６ａと、を有する。すなわち、動力伝達部４は、デフケースシャフト４６ａを有する。デフケースシャフト４６ａは、出力軸線Ｊ３を中心として軸方向に沿って延びる筒状である。デフケースシャフト４６ａは、第７ベアリング５Ｇ、および第８ベアリング５Ｈに回転可能に支持される。リングギヤ４６ｇは、デフケースシャフト４６ａの外周面に設けられる。デフケースシャフト４６ａは、出力軸線Ｊ３を中心としてリングギヤ４６ｇとともに回転する。 The differential case 46 includes a case portion 46b that accommodates a differential mechanism portion 46c therein, and a differential case shaft 46a that protrudes to the other side and the other side in the axial direction with respect to the case portion 46b. That is, the power transmission section 4 includes a differential case shaft 46a. The differential case shaft 46a has a cylindrical shape that extends in the axial direction centering on the output axis J3. The differential case shaft 46a is rotatably supported by a seventh bearing 5G and an eighth bearing 5H. Ring gear 46g is provided on the outer peripheral surface of differential case shaft 46a. The differential case shaft 46a rotates together with the ring gear 46g about the output axis J3.
　一対の出力シャフト４７は、差動装置４ｂに接続される。一対の出力シャフト４７は、差動装置４ｂのデフケース４６から軸方向他方側および他方側に突出する。出力シャフト４７は、デフケースシャフト４６ａの内側に配置される。出力シャフト４７は、デフケースシャフト４６ａの内周面に、ベアリング（図示略）を介して回転可能に支持される。 The pair of output shafts 47 are connected to the differential gear 4b. The pair of output shafts 47 protrude from the differential case 46 of the differential device 4b to the other side in the axial direction and to the other side. The output shaft 47 is arranged inside the differential case shaft 46a. The output shaft 47 is rotatably supported on the inner peripheral surface of the differential case shaft 46a via a bearing (not shown).
　モータ２から出力されるトルクは、モータ２の第２シャフト４４、第１ギヤ４１、第２ギヤ４２、第３シャフト４５および第３ギヤ４３を介して差動装置４ｂのリングギヤ４６ｇに伝達され、差動装置４ｂの差動機構部４６ｃを介して出力シャフト４７に出力される。動力伝達部４の複数のギヤ４１、４２、４３、４６ｇは、第２シャフト４４、第３シャフト４５、デフケースシャフト４６ａの順でモータ２の動力を伝達する。 The torque output from the motor 2 is transmitted to the ring gear 46g of the differential device 4b via the second shaft 44, first gear 41, second gear 42, third shaft 45, and third gear 43 of the motor 2, It is output to the output shaft 47 via the differential mechanism section 46c of the differential device 4b. The plurality of gears 41, 42, 43, and 46g of the power transmission section 4 transmit the power of the motor 2 to the second shaft 44, the third shaft 45, and the differential case shaft 46a in this order.
　＜ハウジング＞
　ハウジング６は、モータカバー６Ａとハウジング本体６Ｂとギヤカバー６Ｃとウォータジャケット６Ｄとを有する。モータカバー６Ａ、ハウジング本体６Ｂ、ギヤカバー６Ｃ、およびウォータジャケット６Ｄは、それぞれ別部材である。モータカバー６Ａは、ハウジング本体６Ｂの軸方向他方側（＋Ｙ側）に配置される。ギヤカバー６Ｃは、ハウジング本体６Ｂの軸方向一方側（－Ｙ側）に配置される。ウォータジャケット６Ｄは、ハウジング本体６Ｂの内部に配置される。 <Housing>
The housing 6 includes a motor cover 6A, a housing body 6B, a gear cover 6C, and a water jacket 6D. The motor cover 6A, the housing body 6B, the gear cover 6C, and the water jacket 6D are each separate members. The motor cover 6A is arranged on the other axial side (+Y side) of the housing body 6B. The gear cover 6C is arranged on one axial side (-Y side) of the housing body 6B. Water jacket 6D is arranged inside housing body 6B.
　ハウジング本体６Ｂは、モータ２を収容し軸方向他方側（＋Ｙ側）に開口する。ハウジング本体６Ｂは、中心軸線Ｊ１を中心とする筒状の外側筒部６５と、外側筒部６５の軸方向一方側（－Ｙ側）に配置され外側筒部６５の軸方向一方側の開口を覆う隔壁６５ａと、隔壁６５ａの外縁から軸方向一方側（－Ｙ側）に延びる第１周壁部６５ｂと、を有する。すなわち、ハウジング６は、隔壁６５ａを有する。 The housing main body 6B accommodates the motor 2 and opens on the other axial side (+Y side). The housing main body 6B includes a cylindrical outer cylinder part 65 centered on the central axis J1, and an opening on one axial side of the outer cylinder part 65, which is arranged on one axial side (-Y side) of the outer cylinder part 65. It has a partition wall 65a that covers the partition wall 65a, and a first peripheral wall portion 65b extending from the outer edge of the partition wall 65a to one side in the axial direction (-Y side). That is, the housing 6 has a partition wall 65a.
　隔壁６５ａには、連通孔６５ｈが設けられる。連通孔６５ｈの内部には、第１ベアリング５Ａ、第２ベアリング５Ｂ、およびシール部材５Ｓが配置される。第１シャフト２１と第２シャフト４４とは、連通孔６５ｈの内部で互いに連結される。なお、図１のシール部材５Ｓは模式化して描画したものであり実際の配置を再現したものではない。連通孔６５ｈの構成については、図４を基に後段において詳細に説明する。 A communication hole 65h is provided in the partition wall 65a. A first bearing 5A, a second bearing 5B, and a seal member 5S are arranged inside the communication hole 65h. The first shaft 21 and the second shaft 44 are connected to each other inside the communication hole 65h. Note that the seal member 5S in FIG. 1 is drawn schematically and does not reproduce the actual arrangement. The configuration of the communication hole 65h will be described in detail later based on FIG. 4.
　外側筒部６５は、モータ２を径方向外側から囲む。外側筒部６５は、ウォータジャケット６Ｄを介してステータ３０を支持する。 The outer cylindrical portion 65 surrounds the motor 2 from the outside in the radial direction. The outer cylindrical portion 65 supports the stator 30 via the water jacket 6D.
　ギヤカバー６Ｃは、ハウジング本体６Ｂの軸方向一方側（－Ｙ側）に配置される。ギヤカバー６Ｃは、隔壁６５ａと対向する対向壁６７と、対向壁６７の外縁から軸方向他方側（＋Ｙ側）に延びる第２周壁部６７ａと、を有する。第２周壁部６７ａの軸方向他方側（＋Ｙ側）の端面は、第１周壁部６５ｂの軸方向一方側（－Ｙ側）の端面に締結される。 The gear cover 6C is arranged on one axial side (-Y side) of the housing body 6B. The gear cover 6C includes an opposing wall 67 that faces the partition wall 65a, and a second peripheral wall portion 67a extending from the outer edge of the opposing wall 67 toward the other axial side (+Y side). The end face of the second peripheral wall portion 67a on the other axial side (+Y side) is fastened to the end face of the first peripheral wall portion 65b on the one axial side (−Y side).
　モータカバー６Ａは、ハウジング本体６Ｂの外側筒部６５の軸方向他方側（＋Ｙ側）の開口を覆う。モータカバー６Ａは、ロータ２０を回転可能に支持する第３ベアリング５Ｃを保持する。 The motor cover 6A covers the opening on the other axial side (+Y side) of the outer cylinder portion 65 of the housing body 6B. The motor cover 6A holds a third bearing 5C that rotatably supports the rotor 20.
　ウォータジャケット６Ｄは、中心軸線Ｊ１を中心とする筒状の内側筒部６４と、内側筒部６４の外周面に設けられる突出リブ６４ａと、を有する。内側筒部６４は、ステータ３０を径方向外側から囲む。内側筒部６４の内径は、ステータコア３２の外径と略一致する。 The water jacket 6D has a cylindrical inner cylinder part 64 centered on the central axis J1, and a protruding rib 64a provided on the outer peripheral surface of the inner cylinder part 64. The inner cylinder portion 64 surrounds the stator 30 from the outside in the radial direction. The inner diameter of the inner cylindrical portion 64 substantially matches the outer diameter of the stator core 32.
　内側筒部６４の内周面は、ステータ３０の外周面と接触する。また、内側筒部６４は、外側筒部６５によって径方向外側から囲まれる。内側筒部６４の外径は、ハウジング本体６Ｂの外側筒部６５の内径より小さい。内側筒部６４と外側筒部６５との間には、水路９３として機能する隙間が設けられる。 The inner circumferential surface of the inner cylindrical portion 64 contacts the outer circumferential surface of the stator 30. Moreover, the inner cylinder part 64 is surrounded by the outer cylinder part 65 from the outside in the radial direction. The outer diameter of the inner cylindrical portion 64 is smaller than the inner diameter of the outer cylindrical portion 65 of the housing body 6B. A gap is provided between the inner cylindrical portion 64 and the outer cylindrical portion 65, which functions as a water channel 93.
　突出リブ６４ａは、中心軸線Ｊ１を中心として螺旋状に延びる。突出リブ６４ａは、径方向外側の端部に位置する先端部を有する。突出リブ６４ａの先端部は、外側筒部６５の内周面に接触するか、又はわずかな隙間を介して外側筒部６５の内周面と対向する。これにより、突出リブ６４ａは、内側筒部６４と外側筒部６５との間の隙間を仕切って水路９３を螺旋状とする。 The protruding rib 64a extends spirally around the central axis J1. The protruding rib 64a has a tip located at the radially outer end. The tip of the protruding rib 64a contacts the inner circumferential surface of the outer cylindrical portion 65, or faces the inner circumferential surface of the outer cylindrical portion 65 with a slight gap therebetween. Thereby, the protruding rib 64a partitions the gap between the inner cylinder part 64 and the outer cylinder part 65, and makes the water channel 93 spiral.
　本実施形態によれば、ハウジング６には、ステータ３０の外周面に沿って延びる水路９３が設けられる。水路９３には、冷却水Ｌが流れる。冷却水Ｌは、例えば、水である。本実施形態によれば、水路９３を流れる冷却水Ｌによってステータ３０を冷却することができる。 According to this embodiment, the housing 6 is provided with a water channel 93 that extends along the outer peripheral surface of the stator 30. Cooling water L flows through the water channel 93 . The cooling water L is, for example, water. According to this embodiment, the stator 30 can be cooled by the cooling water L flowing through the water channel 93.
　本実施形態では、水路９３が螺旋状に延びる場合について説明した。しかしながら、水路９３は、ステータ３０を囲むものであれば、本実施形態に限定されない。水路９３は、軸方向又は周方向に蛇行する流路であってもよい。水路９３の流路構成は、突出リブ６４ａの形状によって決めることができる。 In this embodiment, a case has been described in which the water channel 93 extends in a spiral shape. However, the water channel 93 is not limited to this embodiment as long as it surrounds the stator 30. The water channel 93 may be a meandering channel in the axial direction or the circumferential direction. The flow path configuration of the water channel 93 can be determined by the shape of the protruding rib 64a.
　ハウジング６の内部には、モータ２を収容するモータ室Ｒ１と、動力伝達部４を収容するギヤ室Ｒ２と、が設けられる。モータ室Ｒ１とギヤ室Ｒ２とは、隔壁６５ａによって区画される。 A motor chamber R1 that accommodates the motor 2 and a gear chamber R2 that accommodates the power transmission section 4 are provided inside the housing 6. The motor chamber R1 and the gear chamber R2 are partitioned by a partition wall 65a.
　モータ室Ｒ１は、外側筒部６５によって径方向外側から囲まれ、隔壁６５ａとモータカバー６Ａとによって軸方向に挟まれる空間である。ギヤ室Ｒ２は、径方向において第１周壁部６５ｂおよび第２周壁部６７ａで囲まれ、軸方向において隔壁６５ａと対向壁６７とに挟まれる空間である。ギヤ室Ｒ２は、モータ室Ｒ１の軸方向一方側（－Ｙ側）に配置される。 The motor chamber R1 is a space surrounded from the outside in the radial direction by the outer cylinder portion 65 and sandwiched in the axial direction by the partition wall 65a and the motor cover 6A. The gear chamber R2 is a space surrounded by the first circumferential wall portion 65b and the second circumferential wall portion 67a in the radial direction, and sandwiched between the partition wall 65a and the opposing wall 67 in the axial direction. The gear chamber R2 is arranged on one axial side (-Y side) of the motor chamber R1.
　ギヤ室Ｒ２には、流体Ｏが貯留される。流体Ｏは、例えばオイルである。本実施形態において流体Ｏは、動力伝達部４およびベアリングに対して潤滑油として使用される。流体Ｏとしては、例えば、冷媒および潤滑油の機能を奏するために、比較的粘度の低いオートマチックトランスミッション用潤滑油（ＡＴＦ：Automatic Transmission Fluid）と同等のオイルを用いることが好ましい。 A fluid O is stored in the gear chamber R2. The fluid O is, for example, oil. In this embodiment, the fluid O is used as a lubricating oil for the power transmission section 4 and the bearings. As the fluid O, for example, in order to perform the functions of a refrigerant and a lubricant, it is preferable to use an oil equivalent to automatic transmission fluid (ATF), which has a relatively low viscosity.
　ハウジング６には、流体Ｏが通過する流体経路５０が設けられる。
　なお、本明細書において、「流体経路」とは、ハウジング６内で循環する流体Ｏの経路を意味する。したがって、「流体経路」とは、定常的に一方向に向かう定常的な流体Ｏの流動を形成する管状の流路のみならず、流体Ｏを一時的に滞留させる経路（例えば貯留部）、流体Ｏが滴り落ちる経路、流体Ｏが飛散する経路をも含む概念である。 The housing 6 is provided with a fluid path 50 through which the fluid O passes.
Note that in this specification, the term "fluid path" means a path for the fluid O circulating within the housing 6. Therefore, the term "fluid path" refers not only to a tubular flow path that forms a steady flow of fluid O that constantly goes in one direction, but also to a path that temporarily retains fluid O (for example, a storage section), a fluid This concept also includes a path through which O drips and a path through which fluid O scatters.
　流体経路５０は、第１掻き上げ経路５８と、第２掻き上げ経路５９と、第１供給流路５１と、第２供給流路（流路）５２と、第３供給流路５３と、第４供給流路５４と、第５供給流路５５と、を有する。また、流体経路５０には、第１貯留部（キャッチタンク）８４、および第２貯留部８２が配置される。すなわち、駆動装置１は、第１掻き上げ経路５８、第２掻き上げ経路５９、第１供給流路５１、第２供給流路５２、第３供給流路５３、第４供給流路５４、第５供給流路５５、第１貯留部８４、および第２貯留部８２を有する。第１供給流路５１、第２供給流路５２、第３供給流路５３、第４供給流路５４、および第５供給流路５５には、流体Ｏが流れる。また、第１貯留部８４、および第２貯留部８２には、流体Ｏが溜まる。 The fluid path 50 includes a first raking path 58, a second raking path 59, a first supply path 51, a second supply path (flow path) 52, a third supply path 53, and a second raking path 59. It has a fourth supply flow path 54 and a fifth supply flow path 55. Further, a first storage section (catch tank) 84 and a second storage section 82 are arranged in the fluid path 50 . That is, the drive device 1 includes a first scraping path 58, a second scraping path 59, a first supply channel 51, a second supply channel 52, a third supply channel 53, a fourth supply channel 54, and a 5 supply channel 55, a first storage section 84, and a second storage section 82. Fluid O flows through the first supply channel 51 , the second supply channel 52 , the third supply channel 53 , the fourth supply channel 54 , and the fifth supply channel 55 . Further, fluid O is accumulated in the first storage section 84 and the second storage section 82 .
　第１貯留部８４は、ギヤ室Ｒ２に配置される。第１貯留部８４は、上側に開口するキャッチタンクである。第１貯留部８４は、動力伝達部４の各ギヤ（例えば、リングギヤ４６ｇ、および第２ギヤ４２）にかき上げられた流体Ｏを受ける。 The first storage portion 84 is arranged in the gear chamber R2. The first storage section 84 is a catch tank that opens upward. The first storage section 84 receives the fluid O scooped up by each gear (for example, the ring gear 46g and the second gear 42) of the power transmission section 4.
　図２は、ギヤ室Ｒ２を軸方向一方側（－Ｙ側）から見た正面図である。図３は、ギヤ室Ｒ２を軸方向他方側（＋Ｙ側）から見た背面図である。
　図２および図３に示すように本実施形態の第１貯留部８４は、隔壁６５ａから軸方向一方側（－Ｙ側）に突出する第１リブ８４ｄと、対向壁６７から軸方向他方側（＋Ｙ側）に突出する第２リブ８４ｅと、を有する。第１リブ８４ｄの軸方向一方側端面と第２リブ８４ｅ軸方向他方側端面とは、互いに接触し連結する。 FIG. 2 is a front view of the gear chamber R2 viewed from one axial side (-Y side). FIG. 3 is a rear view of the gear chamber R2 viewed from the other axial side (+Y side).
As shown in FIGS. 2 and 3, the first storage portion 84 of this embodiment includes a first rib 84d that protrudes from the partition wall 65a to one axial side (-Y side), and a first rib 84d that protrudes from the opposite wall 67 to the other axial side (-Y side). +Y side). One axial end surface of the first rib 84d and the other axial end surface of the second rib 84e contact and connect with each other.
　図１に示すように、第２貯留部８２は、ギヤ室Ｒ２の下部領域に設けられる流体溜りである。すなわち、ギヤ室Ｒ２の下部領域には、流体Ｏが溜まる第２貯留部８２が設けられる。第２貯留部８２内には、リングギヤ４６ｇの下側の端部、および第２ギヤ４２の下側の端部が位置する。したがって、リングギヤ４６ｇおよび第２ギヤ４２の一部は、第２貯留部８２に溜る流体Ｏに浸漬される。 As shown in FIG. 1, the second storage portion 82 is a fluid reservoir provided in the lower region of the gear chamber R2. That is, the second storage section 82 in which the fluid O is stored is provided in the lower region of the gear chamber R2. A lower end of the ring gear 46g and a lower end of the second gear 42 are located within the second storage portion 82. Therefore, the ring gear 46g and a portion of the second gear 42 are immersed in the fluid O accumulated in the second storage section 82.
　第１掻き上げ経路５８は、動力伝達部４のギヤ（本実施形態ではリングギヤ４６ｇ、および第２ギヤ４２）の回転によって、第２貯留部８２の流体Ｏを掻き上げて第１貯留部８４に導く経路である。第１掻き上げ経路５８によって流体Ｏを第２貯留部８２から第１貯留部８４に移送することで、第１貯留部８４の貯留量が高まり、第１貯留部８４の流体Ｏの液位が下がる。本実施形態によれば、第１貯留部８４に流体Ｏを貯留することで、第２貯留部８２の液位を下げ、流体Ｏによるリングギヤ４６ｇおよび第２ギヤ４２の撹拌抵抗を低減させることができる。 The first scooping path 58 scrapes up the fluid O in the second storage section 82 and transfers it to the first storage section 84 by the rotation of the gears of the power transmission section 4 (in this embodiment, the ring gear 46g and the second gear 42). It is a path that leads. By transferring the fluid O from the second storage section 82 to the first storage section 84 through the first scooping path 58, the amount of storage in the first storage section 84 increases, and the liquid level of the fluid O in the first storage section 84 increases. Go down. According to this embodiment, by storing the fluid O in the first storage part 84, the liquid level in the second storage part 82 can be lowered, and the stirring resistance of the ring gear 46g and the second gear 42 due to the fluid O can be reduced. can.
　第２掻き上げ経路５９は、動力伝達部４のギヤ（本実施形態ではリングギヤ４６ｇ、および第２ギヤ４２）の回転によって、第２貯留部８２の流体Ｏを掻き上げて第８ベアリング５Ｈに供給する経路である。 The second scooping path 59 scoops up the fluid O in the second storage section 82 and supplies it to the eighth bearing 5H by the rotation of the gears of the power transmission section 4 (in this embodiment, the ring gear 46g and the second gear 42). This is the route to
　図３に示すように、第１供給流路５１、および第３供給流路５３は、ギヤカバー６Ｃの対向壁６７に設けられる。第１供給流路５１は、第１貯留部８４から第４ベアリング５Ｄに向かって延びる。第１供給流路５１は、第１貯留部８４の流体Ｏを第４ベアリング５Ｄに供給する。第３供給流路５３は、第１貯留部８４から第６ベアリング５Ｆに向かって延びる。第３供給流路５３は、第１貯留部８４の流体Ｏを第６ベアリング５Ｆに供給する。 As shown in FIG. 3, the first supply channel 51 and the third supply channel 53 are provided on the opposing wall 67 of the gear cover 6C. The first supply channel 51 extends from the first storage section 84 toward the fourth bearing 5D. The first supply channel 51 supplies the fluid O in the first storage section 84 to the fourth bearing 5D. The third supply channel 53 extends from the first storage section 84 toward the sixth bearing 5F. The third supply channel 53 supplies the fluid O in the first storage section 84 to the sixth bearing 5F.
　図２に示すように、第２供給流路５２、第４供給流路５４、および第５供給流路５５は、ハウジング本体６Ｂの隔壁６５ａに設けられる。第２供給流路５２は、第１貯留部８４から連通孔６５ｈの内周面に向かって延びる。第２供給流路５２の構成については、後段において詳細に説明する。 As shown in FIG. 2, the second supply channel 52, the fourth supply channel 54, and the fifth supply channel 55 are provided in the partition wall 65a of the housing body 6B. The second supply channel 52 extends from the first storage section 84 toward the inner peripheral surface of the communication hole 65h. The configuration of the second supply channel 52 will be described in detail later.
　第４供給流路５４は、第１貯留部８４から第５ベアリング５Ｅに向かって延びる。第４供給流路５４は、第１貯留部８４の流体Ｏを第５ベアリング５Ｅに供給する。第５供給流路５５は、第１貯留部８４から第７ベアリング５Ｇに向かって延びる。第５供給流路５５は、第１貯留部８４の流体Ｏを第７ベアリング５Ｇに供給する。 The fourth supply flow path 54 extends from the first storage section 84 toward the fifth bearing 5E. The fourth supply channel 54 supplies the fluid O in the first storage section 84 to the fifth bearing 5E. The fifth supply channel 55 extends from the first storage section 84 toward the seventh bearing 5G. The fifth supply channel 55 supplies the fluid O in the first storage section 84 to the seventh bearing 5G.
　＜連通孔＞
　図４は、連通孔６５ｈに配置される第１シャフト２１および第２シャフト４４の断面図である。
　連通孔６５ｈは、モータ室Ｒ１とギヤ室Ｒ２とを連通する。連通孔６５ｈの内周面は、中心軸線Ｊ１を中心とする円形である。連通孔６５ｈの内周面は、第１ベアリング５Ａ、第２ベアリング５Ｂ、およびシール部材５Ｓを保持する。 <Communication hole>
FIG. 4 is a sectional view of the first shaft 21 and the second shaft 44 arranged in the communication hole 65h.
The communication hole 65h communicates the motor chamber R1 and the gear chamber R2. The inner circumferential surface of the communication hole 65h is circular centered on the central axis J1. The inner peripheral surface of the communication hole 65h holds the first bearing 5A, the second bearing 5B, and the seal member 5S.
　隔壁６５ａは、連通孔６５ｈの内縁に沿ってギヤ室Ｒ２側（すなわち、軸方向一方側（－Ｙ側））に突出する筒部１１を有する。筒部１１は、中心軸線Ｊ１を中心とする円筒状である。筒部１１は、第１ベアリング５Ａ、および第２ベアリング５Ｂを囲み保持する。本明細書において、筒部１１の内周面とは、すなわち連通孔６５ｈの内周面である。隔壁６５ａに筒部１１が設けられることで、連通孔６５ｈの内周面を軸方向に沿って延長できる。これにより、連通孔６５ｈの内周面に複数のベアリングを安定して保持できる。 The partition wall 65a has a cylindrical portion 11 that protrudes toward the gear chamber R2 side (ie, one axial side (-Y side)) along the inner edge of the communication hole 65h. The cylindrical portion 11 has a cylindrical shape centered on the central axis J1. The cylindrical portion 11 surrounds and holds the first bearing 5A and the second bearing 5B. In this specification, the inner circumferential surface of the cylindrical portion 11 is the inner circumferential surface of the communication hole 65h. By providing the cylindrical portion 11 on the partition wall 65a, the inner peripheral surface of the communication hole 65h can be extended along the axial direction. Thereby, a plurality of bearings can be stably held on the inner peripheral surface of the communication hole 65h.
　連通孔６５ｈの内周面は、第１内周面６６ａと第２内周面６６ｂと第３内周面６６ｃと第４内周面６６ｄと第１段差面６６ｅと第２段差面６６ｆと第３段差面６６ｇとを有する。第１内周面６６ａ、第２内周面６６ｂ、第３内周面６６ｃ、および第４内周面６６ｄは、軸方向他方側（＋Ｙ側）から軸方向一方側（－Ｙ側）に向かってこの順で並ぶ。 The inner circumferential surface of the communication hole 65h includes a first inner circumferential surface 66a, a second inner circumferential surface 66b, a third inner circumferential surface 66c, a fourth inner circumferential surface 66d, a first stepped surface 66e, a second stepped surface 66f, and a third inner circumferential surface 66c. It has a three-step surface 66g. The first inner circumferential surface 66a, the second inner circumferential surface 66b, the third inner circumferential surface 66c, and the fourth inner circumferential surface 66d extend from the other axial side (+Y side) to the one axial side (-Y side). Line up in the order of levers.
　第１内周面６６ａは、第１ベアリング５Ａの外周面を囲む。第１内周面６６ａは、第１ベアリング５Ａを保持する。第１内周面６６ａの直径は、第２内周面６６ｂの直径より大きい。第１内周面６６ａと第２内周面６６ｂとの間には、軸方向他方側（＋Ｙ側）を向く第１段差面６６ｅが設けられる。第１ベアリング５Ａの外輪５Ａａの軸方向一方側端面は、第１段差面６６ｅに押し当てられる。第１ベアリング５Ａは、第１シャフト２１を支持する。 The first inner peripheral surface 66a surrounds the outer peripheral surface of the first bearing 5A. The first inner peripheral surface 66a holds the first bearing 5A. The diameter of the first inner peripheral surface 66a is larger than the diameter of the second inner peripheral surface 66b. A first step surface 66e facing the other axial side (+Y side) is provided between the first inner circumferential surface 66a and the second inner circumferential surface 66b. One axial end surface of the outer ring 5Aa of the first bearing 5A is pressed against the first stepped surface 66e. The first bearing 5A supports the first shaft 21.
　第２内周面６６ｂには、シール部材５Ｓが保持される。第２内周面６６ｂは、シール部材５Ｓを保持する。第２内周面６６ｂの直径は、第３内周面６６ｃの直径より大きい、このため、第２内周面６６ｂと第３内周面６６ｃとの間には、軸方向他方側（＋Ｙ側）を向く第２段差面６６ｆが設けられる。シール部材５Ｓは、第２段差面６６ｆに接触して位置合わせされる。 A seal member 5S is held on the second inner circumferential surface 66b. The second inner peripheral surface 66b holds the seal member 5S. The diameter of the second inner circumferential surface 66b is larger than the diameter of the third inner circumferential surface 66c. Therefore, there is a gap between the second inner circumferential surface 66b and the third inner circumferential surface 66c on the other side in the axial direction (+Y side). ) is provided. The seal member 5S contacts and is aligned with the second step surface 66f.
　第３内周面６６ｃは、連通孔６５ｈの内周面において最も直径が小さい。第３内周面６６ｃは、後述する連結空間Ａを径方向外側から囲む。 The third inner peripheral surface 66c has the smallest diameter on the inner peripheral surface of the communication hole 65h. The third inner circumferential surface 66c surrounds a connection space A, which will be described later, from the outside in the radial direction.
　第４内周面６６ｄは、第２ベアリング５Ｂの外周面を囲む。第４内周面６６ｄは、第２ベアリング５Ｂを保持する。第４内周面６６ｄの直径は、第３内周面６６ｃの直径より大きい。第４内周面６６ｄと第３内周面６６ｃとの間には、軸方向一方側（－Ｙ側）を向く第３段差面６６ｇが設けられる。第２ベアリング５Ｂの外輪５Ｂａの軸方向他方側端面は、第３段差面６６ｇに押し当てられる。第２ベアリング５Ｂは、第２シャフト４４を支持する。 The fourth inner peripheral surface 66d surrounds the outer peripheral surface of the second bearing 5B. The fourth inner peripheral surface 66d holds the second bearing 5B. The diameter of the fourth inner peripheral surface 66d is larger than the diameter of the third inner peripheral surface 66c. A third step surface 66g facing one side in the axial direction (-Y side) is provided between the fourth inner circumferential surface 66d and the third inner circumferential surface 66c. The other end surface of the outer ring 5Ba of the second bearing 5B in the axial direction is pressed against the third step surface 66g. The second bearing 5B supports the second shaft 44.
　第１シャフト２１の軸方向一方側（－Ｙ側）の端部は、連結開口部２１ａを有する。連結開口部２１ａは、軸方向から見て中心軸線Ｊ１を中心とする円形である。連結開口部２１ａは、第１シャフト２１の中空部２１Ｈと繋がる。連結開口部２１ａは、径方向内側を向く内周面を有する。連結開口部２１ａの内周面には、複数のスプライン溝２１ｓが設けられる。複数のスプライン溝２１ｓは、軸方向に延びる。複数のスプライン溝２１ｓは、周方向に沿って並ぶ。 The end of the first shaft 21 on one axial side (-Y side) has a connection opening 21a. The connecting opening 21a has a circular shape centered on the central axis J1 when viewed from the axial direction. The connection opening 21a is connected to the hollow portion 21H of the first shaft 21. The connection opening 21a has an inner circumferential surface facing radially inward. A plurality of spline grooves 21s are provided on the inner peripheral surface of the connection opening 21a. The plurality of spline grooves 21s extend in the axial direction. The plurality of spline grooves 21s are arranged along the circumferential direction.
　第２シャフト４４の軸方向他方側（＋Ｙ側）の端部は、連結凸部４４ａを有する。連結凸部４４ａは、中心軸線Ｊ１を中心とする円柱状である。連結凸部４４ａは、軸方向他方側（＋Ｙ側）を向く先端面４４ｂと、径方向外側を向く外周面とを有する。連結凸部４４ａの外周面には、複数のスプライン突起４４ｓが設けられる。複数のスプライン突起４４ｓは、軸方向に延びる。複数のスプライン突起４４ｓは、周方向に沿って並ぶ。 The end of the second shaft 44 on the other axial side (+Y side) has a connecting convex portion 44a. The connecting convex portion 44a has a cylindrical shape centered on the central axis J1. The connecting convex portion 44a has a distal end surface 44b facing the other side in the axial direction (+Y side) and an outer circumferential surface facing outward in the radial direction. A plurality of spline protrusions 44s are provided on the outer peripheral surface of the connecting convex portion 44a. The plurality of spline protrusions 44s extend in the axial direction. The plurality of spline protrusions 44s are arranged along the circumferential direction.
　図５は、連結開口部２１ａと連結凸部４４ａとの連結部を示す断面図である。
　第１シャフト２１と第２シャフト４４とは、連結開口部２１ａのスプライン溝２１ｓと連結凸部４４ａのスプライン突起４４ｓとの噛み合いにより互いに連結される。以下の説明において、スプライン溝２１ｓとスプライン突起４４ｓとが噛み合って連結される部分を連結部３とする。 FIG. 5 is a sectional view showing a connecting portion between the connecting opening 21a and the connecting convex portion 44a.
The first shaft 21 and the second shaft 44 are connected to each other by meshing with the spline groove 21s of the connection opening 21a and the spline protrusion 44s of the connection convex portion 44a. In the following description, the portion where the spline groove 21s and the spline protrusion 44s engage and are connected will be referred to as a connecting portion 3.
　スプライン溝２１ｓは、一様な断面形状で軸方向に沿って延びる。同様に、スプライン突起４４ｓは、一様な断面形状で軸方向に沿って延びる。１つのスプライン溝２１ｓには、１つのスプライン突起４４ｓが挿入される。スプライン溝２１ｓの径方向内側を向く底面の径は、スプライン突起４４ｓの径方向外側を向く先端面の径より大きい。また、スプライン溝２１ｓの幅寸法は、スプライン突起４４ｓの幅寸法よりも大きい。このため、スプライン溝２１ｓの内側面とスプライン突起４４ｓの外側面との間には、隙間３ａが設けられる。流体Ｏは、隙間３ａを通って連結部３の軸方向一方側の端部と他方側の端部との間で相互に移動する。 The spline groove 21s has a uniform cross-sectional shape and extends along the axial direction. Similarly, the spline protrusion 44s has a uniform cross-sectional shape and extends in the axial direction. One spline projection 44s is inserted into one spline groove 21s. The diameter of the bottom surface of the spline groove 21s facing radially inward is larger than the diameter of the tip surface facing radially outside of the spline protrusion 44s. Moreover, the width dimension of the spline groove 21s is larger than the width dimension of the spline protrusion 44s. Therefore, a gap 3a is provided between the inner surface of the spline groove 21s and the outer surface of the spline projection 44s. The fluid O mutually moves between one end and the other end of the connecting portion 3 in the axial direction through the gap 3a.
　図４に示すように、第１シャフト２１と第２シャフト４４とは、連結部３において周方向の相対的な移動が制限される。このため、第１シャフト２１と第２シャフト４４とは、中心軸線Ｊ１周りを同期回転する。また、第１シャフト２１と第２シャフト４４とは、連結部３において、軸方向の相対的な移動を許容する。 As shown in FIG. 4, the relative movement of the first shaft 21 and the second shaft 44 in the circumferential direction is restricted at the connecting portion 3. Therefore, the first shaft 21 and the second shaft 44 rotate synchronously around the central axis J1. Further, the first shaft 21 and the second shaft 44 allow relative movement in the axial direction in the connecting portion 3.
　本実施形態では、第１ギヤ４１および第２ギヤ４２としてヘリカルギヤを採用できる。このため、第１ギヤ４１は、駆動時に第２ギヤ４２から軸方向を向く反力を受ける。本実施形態によれば、第１シャフト２１と第２シャフト４４とが、連結部３において軸方向に相対的に移動可能であるため、第１ギヤ４１に付与される軸方向の力が、連結部３を介して第１シャフト２１に伝わることを抑制できる。このため、第２シャフト４４を支持するベアリング５Ａ、５Ｃに大きなスラスト荷重が付与されることを抑制できる。 In this embodiment, helical gears can be employed as the first gear 41 and the second gear 42. Therefore, the first gear 41 receives a reaction force directed in the axial direction from the second gear 42 during driving. According to the present embodiment, since the first shaft 21 and the second shaft 44 are relatively movable in the axial direction in the connecting portion 3, the axial force applied to the first gear 41 is It is possible to suppress the transmission of the heat to the first shaft 21 via the portion 3 . Therefore, it is possible to suppress a large thrust load from being applied to the bearings 5A, 5C that support the second shaft 44.
　第１シャフト２１の軸方向一方側（－Ｙ側）の端部は、先端に向かうに従い細くなる段差形状を有する。第１シャフト２１は、第１外周面２１ｄと第２外周面２１ｅと第３外周面２１ｆとを有する。第１外周面２１ｄ、第２外周面２１ｅ、および第３外周面２１ｆは、は、軸方向他方側（＋Ｙ側）から一方側に向かってこの順で並ぶ。第１外周面２１ｄ、第２外周面２１ｅ、および第３外周面２１ｆは、この順で直径が小さくなる。 The end of the first shaft 21 on one axial side (−Y side) has a stepped shape that becomes narrower toward the tip. The first shaft 21 has a first outer peripheral surface 21d, a second outer peripheral surface 21e, and a third outer peripheral surface 21f. The first outer circumferential surface 21d, the second outer circumferential surface 21e, and the third outer circumferential surface 21f are arranged in this order from the other axial side (+Y side) to the one side. The diameters of the first outer circumferential surface 21d, the second outer circumferential surface 21e, and the third outer circumferential surface 21f decrease in this order.
　第２外周面２１ｅは、連通孔６５ｈの第１内周面６６ａと径方向に対向する。第２外周面２１ｅには、第１ベアリング５Ａが装着される。すなわち、第２外周面２１ｅは、第１ベアリング５Ａによって囲まれる。第２外周面２１ｅと第１外周面２１ｄと間には、軸方向一方側（－Ｙ側）を向く第４段差面２１ｇが設けられる。第１ベアリング５Ａの内輪５Ａｃの軸方向一方側端面は、第４段差面２１ｇに押し当てられる。 The second outer peripheral surface 21e faces the first inner peripheral surface 66a of the communication hole 65h in the radial direction. The first bearing 5A is mounted on the second outer peripheral surface 21e. That is, the second outer peripheral surface 21e is surrounded by the first bearing 5A. A fourth step surface 21g facing one side in the axial direction (-Y side) is provided between the second outer peripheral surface 21e and the first outer peripheral surface 21d. One axial end surface of the inner ring 5Ac of the first bearing 5A is pressed against the fourth step surface 21g.
　第３外周面２１ｆは、第１シャフト２１の軸方向一方側（－Ｙ側）の端部に位置する。第３外周面２１ｆは、連通孔６５ｈの第２内周面６６ｂと径方向に対向する。第３外周面２１ｆには、シール部材５Ｓの内端が接触する。第１シャフト２１の回転に伴い、第３外周面２１ｆは、シール部材５Ｓと摺動する。 The third outer circumferential surface 21f is located at one end of the first shaft 21 in the axial direction (-Y side). The third outer peripheral surface 21f faces the second inner peripheral surface 66b of the communication hole 65h in the radial direction. The inner end of the seal member 5S contacts the third outer peripheral surface 21f. As the first shaft 21 rotates, the third outer peripheral surface 21f slides on the seal member 5S.
　連通孔６５ｈにおける第１ベアリング５Ａと第２ベアリング５Ｂの軸方向の間には、連結空間Ａが設けられる。本実施形態において、第１ベアリング５Ａと第２ベアリング５Ｂとの軸方向の間の空間は、シール部材５Ｓによって２つに区画される。具体的には、軸方向において第１ベアリング５Ａとシール部材５Ｓとに挟まれる空間と、軸方向において第２ベアリング５Ｂとシール部材５Ｓとに挟まれる空間の２つに区画される。本実施形態の連結空間Ａは、軸方向において第２ベアリング５Ｂとシール部材５Ｓとに挟まれる空間である。すなわち、連結空間Ａには、連結開口部２１ａが開口する。連結空間Ａは、径方向において連通孔６５ｈの第３内周面６６ｃと第２シャフト４４又は第１シャフト２１の外周面とに挟まれ、軸方向において第２ベアリング５Ｂとシール部材５Ｓとに挟まれる。連結空間Ａには、後述する第２供給流路５２の第１流路５２ａを介してギヤ室Ｒ２から流体Ｏが供給される。 A connection space A is provided between the first bearing 5A and the second bearing 5B in the axial direction in the communication hole 65h. In this embodiment, the space between the first bearing 5A and the second bearing 5B in the axial direction is divided into two by the seal member 5S. Specifically, it is divided into two spaces: a space sandwiched between the first bearing 5A and the seal member 5S in the axial direction, and a space sandwiched between the second bearing 5B and the seal member 5S in the axial direction. The connection space A of this embodiment is a space sandwiched between the second bearing 5B and the seal member 5S in the axial direction. That is, in the connection space A, the connection opening 21a opens. The connection space A is sandwiched between the third inner peripheral surface 66c of the communication hole 65h and the outer peripheral surface of the second shaft 44 or the first shaft 21 in the radial direction, and between the second bearing 5B and the seal member 5S in the axial direction. It will be done. Fluid O is supplied to the connection space A from the gear chamber R2 via a first flow path 52a of a second supply flow path 52, which will be described later.
　なお、本明細書において連結空間Ａは、第１シャフト２１および第２シャフト４４の内部を含まない。連結空間Ａは、径方向において、連通孔６５ｈの内周面の径方向内側、かつ第１シャフト２１の外周面、又は第２シャフト４４の外周面の径方向外側の空間である。すなわち、連結空間Ａは、連通孔６５ｈにおける第１ベアリング５Ａと第２ベアリング５Ｂの軸方向の間、かつ、連通孔６５ｈの内周面と第１シャフト２１の外周面、又は第２シャフト４４の外周面との径方向の間に設けられる。 Note that in this specification, the connection space A does not include the insides of the first shaft 21 and the second shaft 44. The connection space A is a space radially inside the inner peripheral surface of the communication hole 65h and radially outside the outer peripheral surface of the first shaft 21 or the second shaft 44. That is, the connection space A is between the first bearing 5A and the second bearing 5B in the communication hole 65h in the axial direction, and between the inner peripheral surface of the communication hole 65h and the outer peripheral surface of the first shaft 21 or the second shaft 44. It is provided between the outer circumferential surface and the outer peripheral surface in the radial direction.
　本実施形態の連通孔６５ｈには、シール部材５Ｓが設けられる。シール部材５Ｓは、連通孔６５ｈの内周面と第１シャフト２１の外周面との間の隙間を封止する。本実施形態によれば、連結空間Ａに流入した流体Ｏが、ベアリング５Ａを通過してモータ室Ｒ１へと流れることを防ぐことができる。すなわち、連結空間Ａに流入した流体Ｏを連結部３および中空部２１Ｈへと導きやすく、ひいてはモータ２の冷却を好適に行うことができる。また、シール部材５Ｓが連結空間Ａに流体Ｏを留めることで、多くの流体Ｏを第２ベアリング５Ｂに供給できる。 A seal member 5S is provided in the communication hole 65h of this embodiment. The seal member 5S seals the gap between the inner peripheral surface of the communication hole 65h and the outer peripheral surface of the first shaft 21. According to this embodiment, the fluid O that has flowed into the connection space A can be prevented from passing through the bearing 5A and flowing into the motor chamber R1. That is, the fluid O that has flowed into the connection space A can be easily guided to the connection part 3 and the hollow part 21H, and the motor 2 can be cooled suitably. In addition, since the seal member 5S retains the fluid O in the connection space A, a large amount of fluid O can be supplied to the second bearing 5B.
　本実施形態によれば、シール部材５Ｓは、第１ベアリング５Ａと第２ベアリング５Ｂとの間に位置する。また、本実施形態において、連結空間Ａは、シール部材５Ｓと第２ベアリング５Ｂとの間に設けられる。 According to this embodiment, the seal member 5S is located between the first bearing 5A and the second bearing 5B. Moreover, in this embodiment, the connection space A is provided between the seal member 5S and the second bearing 5B.
　図６に変形例として示すように、シール部材２０５Ｓは、第１ベアリング５Ａ、および第２ベアリング５Ｂよりも軸方向他方側（＋Ｙ側）に配置されていてもよい。この場合、連結空間Ａに流入する流体Ｏを、第２ベアリング５Ｂのみならず第１ベアリング５Ａにも供給することができ、第１ベアリング５Ａおよび第２ベアリング５Ｂを潤滑できる。なお、本変形例の連結空間Ａは、径方向において連通孔６５ｈの内周面と第２シャフト４４、又は第１シャフト２１の外周面とに挟まれ、軸方向において第１ベアリング５Ａと第２ベアリング５Ｂとに挟まれる空間である。 As shown as a modification in FIG. 6, the seal member 205S may be arranged on the other axial side (+Y side) of the first bearing 5A and the second bearing 5B. In this case, the fluid O flowing into the connection space A can be supplied not only to the second bearing 5B but also to the first bearing 5A, thereby lubricating the first bearing 5A and the second bearing 5B. The connection space A of this modification is sandwiched between the inner peripheral surface of the communication hole 65h and the outer peripheral surface of the second shaft 44 or the first shaft 21 in the radial direction, and is sandwiched between the first bearing 5A and the second shaft in the axial direction. This is the space sandwiched between the bearing 5B and the bearing 5B.
　図４に示すように、本実施形態によれば、シール部材５Ｓは、連通孔６５ｈの内周面に保持され、第１シャフト２１の外周面に接触する。また、第１シャフト２１は、シール部材５Ｓの接触する部分（第３外周面２１ｆ）の外径が、第１ベアリング５Ａに支持される部分（第２外周面２１ｅ）の外径より小さい。第１シャフト２１が回転すると、シール部材５Ｓと第３外周面２１ｆとが摺動する。第３外周面２１ｆの直径を小さくすることで、シール部材５Ｓと第３外周面２１ｆとの摺動速度を小さくすることができ、摺動に伴う発熱を抑制できる。また、第３外周面２１ｆの直径を小さくすることで、摺動時の動摩擦力に起因して第１シャフト２１に付与されるトルクを小さくすることができ、第１シャフト２１の回転効率を高めることができる。一方で、第２外周面２１ｅの外形を第３外周面２１ｆより大きくすることで、第２外周面２１ｅの内側で第１シャフト２１の厚さを十分に確保できる。これにより、第１シャフト２１の第１ベアリング５Ａで支持される部分の剛性を高め、第１シャフト２１を第１ベアリング５Ａで安定して保持させることができる。 As shown in FIG. 4, according to the present embodiment, the seal member 5S is held on the inner peripheral surface of the communication hole 65h and contacts the outer peripheral surface of the first shaft 21. Further, in the first shaft 21, the outer diameter of the portion (third outer circumferential surface 21f) in contact with the seal member 5S is smaller than the outer diameter of the portion (second outer circumferential surface 21e) supported by the first bearing 5A. When the first shaft 21 rotates, the seal member 5S and the third outer peripheral surface 21f slide. By reducing the diameter of the third outer circumferential surface 21f, the sliding speed between the seal member 5S and the third outer circumferential surface 21f can be reduced, and heat generation due to sliding can be suppressed. Furthermore, by reducing the diameter of the third outer circumferential surface 21f, it is possible to reduce the torque applied to the first shaft 21 due to the dynamic friction force during sliding, thereby increasing the rotational efficiency of the first shaft 21. be able to. On the other hand, by making the outer shape of the second outer circumferential surface 21e larger than the third outer circumferential surface 21f, a sufficient thickness of the first shaft 21 can be ensured inside the second outer circumferential surface 21e. Thereby, the rigidity of the portion of the first shaft 21 supported by the first bearing 5A can be increased, and the first shaft 21 can be stably held by the first bearing 5A.
　＜第２供給流路（流路）＞
　第２供給流路５２は、第１流路５２ａと第２流路５２ｅと第３流路５２ｄとを有する。第２供給流路５２は、第１流路５２ａおよび第２流路５２ｅにおいて、ギヤ室Ｒ２から連結部３を通ってモータ室Ｒ１に達する。また、本実施形態の第２供給流路５２は、さらに第３流路５２ｄを有し、第２ベアリング５Ｂを潤滑させる。 <Second supply flow path (flow path)>
The second supply channel 52 has a first channel 52a, a second channel 52e, and a third channel 52d. The second supply flow path 52 reaches the motor chamber R1 from the gear chamber R2 through the connecting portion 3 in the first flow path 52a and the second flow path 52e. Further, the second supply flow path 52 of this embodiment further includes a third flow path 52d, which lubricates the second bearing 5B.
　第１流路５２ａは、ギヤ室Ｒ２と連結空間Ａとを繋ぐ。第２流路５２ｅは、連結空間Ａと第１シャフト２１の中空部（内部）２１Ｈとを繋ぐ。第３流路５２ｄは、連結空間Ａとギヤ室Ｒ２とを繋ぐ。 The first flow path 52a connects the gear chamber R2 and the connection space A. The second flow path 52e connects the connection space A and the hollow portion (inside) 21H of the first shaft 21. The third flow path 52d connects the connection space A and the gear chamber R2.
　図２に示すように、第１流路５２ａは、孔部８４ａと、第１凹溝（凹溝）１１ａと第２凹溝１１ｂとを有する。
　孔部８４ａは、ハウジング６の隔壁６５ａに設けられる。孔部８４ａは、ドリル加工によって形成される。孔部８４ａの上端部は、第１貯留部８４に繋がる。孔部８４ａの上端部は、第１貯留部８４の底面に開口する。孔部８４ａの下端部は、筒部１１の内周面に繋がる。すなわち、孔部８４ａは、筒部１１を径方向に貫通する。また、孔部８４ａは、第１貯留部８４から筒部１１の内周面に延びる。孔部８４ａは、第１貯留部８４と筒部１１の内周面とを繋ぐ。 As shown in FIG. 2, the first flow path 52a has a hole 84a, a first groove (groove) 11a, and a second groove 11b.
The hole 84a is provided in the partition wall 65a of the housing 6. The hole 84a is formed by drilling. The upper end of the hole 84 a is connected to the first storage section 84 . The upper end of the hole 84a opens to the bottom surface of the first storage section 84. The lower end of the hole 84a is connected to the inner circumferential surface of the cylindrical portion 11. That is, the hole portion 84a penetrates the cylindrical portion 11 in the radial direction. Further, the hole 84a extends from the first storage portion 84 to the inner circumferential surface of the cylindrical portion 11. The hole portion 84a connects the first storage portion 84 and the inner peripheral surface of the cylindrical portion 11.
　図４に示すように、本実施形態によれば、筒部１１には、径方向に沿って延びて第１流路５２ａの一部を構成する孔部８４ａが設けられる。第１流路５２ａの一部を孔部８４ａとすることで、第１貯留部８４から連結空間Ａに安定した流体Ｏの供給ができる。 As shown in FIG. 4, according to the present embodiment, the cylindrical portion 11 is provided with a hole 84a that extends along the radial direction and constitutes a part of the first flow path 52a. By forming a part of the first flow path 52a as the hole 84a, the fluid O can be stably supplied from the first storage section 84 to the connection space A.
　なお、本実施形態では、第１流路５２ａが孔部８４ａにおいて筒部１１の内外を貫通する場合について説明した。しかしながら、第１流路５２ａは、筒部１１に設けられる切欠部によって筒部１１の内外を貫通してもよい。すなわち、筒部１１には、径方向に沿って延びて第１流路５２ａの一部を構成する切欠部が設けられていてもよい。また、本実施形態において、第１流路５２ａは、孔部８４ａにおいて隔壁６５ａの内部を貫通する。しかしながら、第１流路５２ａは、孔部８４ａに替えて、隔壁６５ａの表面に設けられる溝部又はリブを有していてもよい。すなわち、隔壁６５ａには、第１貯留部８４から筒部１１に向かって延びて第１流路５２ａの一部を構成する溝部又はリブを有していてもよい。 In addition, in this embodiment, the case where the first flow path 52a penetrates the inside and outside of the cylindrical part 11 at the hole 84a has been described. However, the first flow path 52a may penetrate inside and outside of the cylindrical portion 11 by a notch provided in the cylindrical portion 11. That is, the cylindrical portion 11 may be provided with a notch that extends along the radial direction and constitutes a part of the first flow path 52a. Further, in this embodiment, the first flow path 52a penetrates the inside of the partition wall 65a at the hole 84a. However, the first flow path 52a may have a groove or a rib provided on the surface of the partition wall 65a instead of the hole 84a. That is, the partition wall 65a may have a groove or a rib that extends from the first storage section 84 toward the cylindrical section 11 and constitutes a part of the first flow path 52a.
　第１凹溝１１ａは、筒部１１の内周面に設けられる。本実施形態の第１凹溝１１ａは、連通孔６５ｈの第４内周面６６ｄに設けられる。第１凹溝１１ａは、軸方向に沿って延びる。第１凹溝１１ａは、第４内周面６６ｄの軸方向の全長に亘って設けられる。 The first groove 11a is provided on the inner circumferential surface of the cylindrical portion 11. The first groove 11a of this embodiment is provided on the fourth inner peripheral surface 66d of the communication hole 65h. The first groove 11a extends along the axial direction. The first groove 11a is provided over the entire length of the fourth inner peripheral surface 66d in the axial direction.
　上述したように、第４内周面６６ｄは、第２ベアリング５Ｂを径方向外側から囲む。このため、第１凹溝１１ａは、第２ベアリング５Ｂの外周面によって覆われる。第１凹溝１１ａに達する流体Ｏは、第１凹溝１１ａの内側面と第２ベアリング５Ｂの外周面とで囲まれる空間を流れる。 As described above, the fourth inner peripheral surface 66d surrounds the second bearing 5B from the outside in the radial direction. Therefore, the first groove 11a is covered by the outer peripheral surface of the second bearing 5B. The fluid O that reaches the first groove 11a flows through a space surrounded by the inner surface of the first groove 11a and the outer peripheral surface of the second bearing 5B.
　第１凹溝１１ａは、径方向内側を向く底面１１ｃを有する。底面１１ｃには、孔部８４ａが開口する。すなわち、孔部８４ａは、第１凹溝１１ａの底面１１ｃに開口する。孔部８４ａを第４内周面６６ｄに直接的に開口させると、孔部８４ａの開口が第２ベアリング５Ｂの外周面によって覆われて、孔部８４ａから連結空間Ａへの流体Ｏの供給が円滑に行われない。本実施形態によれば、第４内周面６６ｄに第１凹溝１１ａを設け、孔部８４ａを第１凹溝１１ａの底面１１ｃに開口させることで、孔部８４ａの開口から流体Ｏを円滑に供給することができる。 The first groove 11a has a bottom surface 11c facing radially inward. A hole 84a is opened in the bottom surface 11c. That is, the hole 84a opens to the bottom surface 11c of the first groove 11a. When the hole 84a is opened directly into the fourth inner peripheral surface 66d, the opening of the hole 84a is covered by the outer peripheral surface of the second bearing 5B, and the fluid O is not supplied from the hole 84a to the connection space A. It's not done smoothly. According to the present embodiment, the first groove 11a is provided in the fourth inner circumferential surface 66d, and the hole 84a is opened at the bottom surface 11c of the first groove 11a, thereby allowing fluid O to flow smoothly from the opening of the hole 84a. can be supplied to
　第２凹溝１１ｂは、連通孔６５ｈの内周面であって第３段差面６６ｇに設けられる。第２凹溝１１ｂは、径方向に沿って延びる。第２凹溝１１ｂの径方向外側の端部は、第１凹溝１１ａの軸方向他方側（＋Ｙ側）の端部に繋がる。第２凹溝１１ｂの径方向内側の端部は、連結空間Ａに繋がる。 The second groove 11b is provided on the third step surface 66g, which is the inner peripheral surface of the communication hole 65h. The second groove 11b extends in the radial direction. The radially outer end of the second groove 11b is connected to the end of the first groove 11a on the other axial side (+Y side). A radially inner end of the second groove 11b is connected to the connection space A.
　上述したように、第３段差面６６ｇは、第２ベアリング５Ｂの外輪５Ｂａと接触する。このため、第２凹溝１１ｂは、第２ベアリング５Ｂの外輪５Ｂａによって覆われる。第２凹溝１１ｂに達する流体Ｏは、第２凹溝１１ｂの内側面と第２ベアリング５Ｂの外輪５Ｂａとで囲まれる空間を流れる。 As described above, the third step surface 66g contacts the outer ring 5Ba of the second bearing 5B. Therefore, the second groove 11b is covered by the outer ring 5Ba of the second bearing 5B. The fluid O reaching the second groove 11b flows through a space surrounded by the inner surface of the second groove 11b and the outer ring 5Ba of the second bearing 5B.
　第２流路５２ｅは、流入流路５２ｂと流出流路５２ｃとを有する。流入流路５２ｂ、および流出流路５２ｃは、ともに連結空間Ａと第１シャフト２１の中空部２１Ｈとを繋ぐ流路である。流入流路５２ｂは、連結空間Ａから中空部２１Ｈに向かって流体Ｏを流す経路である。一方で、流出流路５２ｃは、中空部２１Ｈから連結空間Ａに向かって流体Ｏを流す経路である。流入流路５２ｂ、および流出流路５２ｃは、ともにスプライン溝２１ｓとスプライン突起４４ｓとの間を通る。 The second channel 52e has an inflow channel 52b and an outflow channel 52c. Both the inflow channel 52b and the outflow channel 52c are channels that connect the connection space A and the hollow portion 21H of the first shaft 21. The inflow channel 52b is a path through which the fluid O flows from the connection space A toward the hollow portion 21H. On the other hand, the outflow channel 52c is a path through which the fluid O flows from the hollow portion 21H toward the connection space A. Both the inflow channel 52b and the outflow channel 52c pass between the spline groove 21s and the spline protrusion 44s.
　図４に二点鎖線の矢印で示すように、第２供給流路５２は、変形例の第１流路２５２ａを有していてもよい。上述の実施形態と同様に、変形例の第１流路２５２ａは、連結空間Ａとギヤ室Ｒ２とを繋ぐ。変形例の第１流路２５２ａは、第２ベアリング５Ｂの内輪５Ｂｃと外輪５Ｂａとの間に設けられる流路である。すなわち、第１流路２５２ａは、第２ベアリング５Ｂを含む流路である。本実施形態によれば、第１流路２５２ａに流体Ｏが流れることで、第２ベアリング５Ｂを潤滑できる。 As shown by the two-dot chain arrow in FIG. 4, the second supply flow path 52 may include a first flow path 252a of a modified example. Similar to the embodiment described above, the first flow path 252a of the modified example connects the connection space A and the gear chamber R2. The first flow path 252a of the modified example is a flow path provided between the inner ring 5Bc and the outer ring 5Ba of the second bearing 5B. That is, the first flow path 252a is a flow path that includes the second bearing 5B. According to this embodiment, the second bearing 5B can be lubricated by the fluid O flowing through the first flow path 252a.
　第２流路５２ｅにおいて、流体Ｏは、流入流路５２ｂと流出流路５２ｃとを同時に流れ得る。連結空間Ａに溜る流体Ｏが比較的多く、中空部２１Ｈに留まる流体Ｏが比較的少ない場合、流入流路５２ｂにより多くの流体Ｏが流れる。反対に、連結空間Ａに溜る流体Ｏが比較的少なく、中空部２１Ｈに留まる流体Ｏが比較的多い場合、流出流路５２ｃにより多くの流体Ｏが流れる。 In the second channel 52e, the fluid O can flow through the inflow channel 52b and the outflow channel 52c simultaneously. When the amount of fluid O accumulated in the connection space A is relatively large and the amount of fluid O remaining in the hollow portion 21H is relatively small, more fluid O flows into the inflow channel 52b. On the other hand, when the amount of fluid O accumulated in the connection space A is relatively small and the amount of fluid O remaining in the hollow portion 21H is relatively large, more fluid O flows through the outflow channel 52c.
　本実施形態によれば、流体Ｏが第２流路５２ｅを流れることで、連結部３に流体Ｏを供給することができる。これにより、スプライン溝２１ｓとスプライン突起４４ｓとの焼き付きを抑制するとともに、スプライン溝２１ｓとスプライン突起４４ｓとの軸方向の滑りを促すことができる。これにより、第２シャフト４４に軸方向の力が付与される場合でも、この力が第１シャフト２１に伝わることを抑制できる。さらに、スプライン溝２１ｓとスプライン突起４４ｓとの間に流体Ｏを充填することができ、第１シャフト２１の回転方向が切り替わる場合などの連結部３の衝撃を緩和できる。 According to this embodiment, the fluid O can be supplied to the connecting portion 3 by flowing through the second flow path 52e. Thereby, it is possible to suppress seizure between the spline groove 21s and the spline protrusion 44s, and to promote sliding between the spline groove 21s and the spline protrusion 44s in the axial direction. Thereby, even if an axial force is applied to the second shaft 44, this force can be suppressed from being transmitted to the first shaft 21. Furthermore, the fluid O can be filled between the spline groove 21s and the spline protrusion 44s, and the impact on the connecting portion 3 when the rotation direction of the first shaft 21 is switched can be alleviated.
　本実施形態において、第１シャフト２１は、モータ室Ｒ１に配置される。すなわち、第１シャフト２１の内部の中空部２１Ｈは、モータ室Ｒ１の一部である。本実施形態によれば、第２流路５２ｅは、連結空間Ａとモータ室Ｒ１とを繋ぐ。このため、ギヤ室Ｒ２の流体Ｏを、連結空間Ａを介してモータ室Ｒ１に移動させることができ、流体Ｏをモータ２の冷却および第３ベアリング５Ｃの潤滑に利用できる。 In this embodiment, the first shaft 21 is arranged in the motor chamber R1. That is, the hollow portion 21H inside the first shaft 21 is a part of the motor chamber R1. According to this embodiment, the second flow path 52e connects the connection space A and the motor chamber R1. Therefore, the fluid O in the gear chamber R2 can be moved to the motor chamber R1 via the connection space A, and the fluid O can be used for cooling the motor 2 and lubricating the third bearing 5C.
　本実施形態の第１流路５２ａと第２流路５２ｅとは、連結空間Ａにおいて接続される。したがって、第２供給流路５２は、第１流路５２ａと第２流路５２ｅとの接続部で、連結空間Ａを通過するように設けられる。連結空間Ａには、連結開口部２１ａが開口する。この連結空間Ａの流体Ｏは、連結部３に供給される。本実施形態の第２供給流路５２によれば、連結部３に流体Ｏを供給しつつ、第１流路５２ａおよび第２流路５２ｅによってモータ室Ｒ１とギヤ室Ｒ２との間で流体Ｏを移動させることができる。このため、連結部３に流体Ｏを供給する流路とモータ室Ｒ１とギヤ室Ｒ２とを繋ぐ流路とを別々に設ける場合と比較して、第２供給流路５２の構造を簡素化することができ。結果的に、第２供給流路５２が設けられるハウジング６の小型化を図ることができる。 The first flow path 52a and the second flow path 52e of this embodiment are connected in the connection space A. Therefore, the second supply flow path 52 is provided so as to pass through the connection space A at the connection portion between the first flow path 52a and the second flow path 52e. A connection opening 21a opens in the connection space A. The fluid O in this connection space A is supplied to the connection part 3. According to the second supply flow path 52 of the present embodiment, while supplying the fluid O to the connecting portion 3, the first flow path 52a and the second flow path 52e supply the fluid O between the motor chamber R1 and the gear chamber R2. can be moved. For this reason, the structure of the second supply flow path 52 is simplified compared to the case where a flow path for supplying the fluid O to the connecting portion 3 and a flow path connecting the motor chamber R1 and the gear chamber R2 are provided separately. It is possible. As a result, the housing 6 in which the second supply channel 52 is provided can be downsized.
　本実施形態の第２供給流路５２では、第１流路５２ａがギヤ室Ｒ２から連結空間Ａに流体Ｏを供給し、第２流路５２ｅが連結空間Ａからモータ室Ｒ１に流体Ｏを供給する。このため、ギヤ室Ｒ２の流体Ｏを連結部３の潤滑を行いつつ、モータ室Ｒ１に送ることができる。 In the second supply flow path 52 of this embodiment, the first flow path 52a supplies fluid O from the gear chamber R2 to the connection space A, and the second flow path 52e supplies fluid O from the connection space A to the motor chamber R1. do. Therefore, the fluid O in the gear chamber R2 can be sent to the motor chamber R1 while lubricating the connecting portion 3.
　本実施形態によれば、連結開口部２１ａが第１シャフト２１の中空部２１Ｈに繋がる。このため、第１貯留部８４から連結部３への流体Ｏの供給が滞った場合に、中空部２１Ｈの流体Ｏは、流出流路５２ｃを流れて連結空間Ａに達する。すなわち、中空部２１Ｈに留まる流体Ｏが、スプライン溝２１ｓとスプライン突起４４ｓとの隙間を徐々に伝わり、連結部３を潤滑することができる。 According to this embodiment, the connection opening 21a is connected to the hollow portion 21H of the first shaft 21. Therefore, when the supply of fluid O from the first storage section 84 to the connection section 3 is delayed, the fluid O in the hollow section 21H flows through the outflow channel 52c and reaches the connection space A. That is, the fluid O remaining in the hollow portion 21H can gradually travel through the gap between the spline groove 21s and the spline protrusion 44s, thereby lubricating the connecting portion 3.
　本実施形態の第２シャフト４４は、中実のシャフトである。このため、第１シャフト２１の中空部２１Ｈに溜る流体Ｏが、第２シャフト４４の内部に流入することがない。本実施形態によれば、中空部２１Ｈに溜る流体Ｏを中空部２１Ｈの軸方向他方側へと導きやすく、モータ２の冷却および第３ベアリング５Ｃの潤滑を好適に行うことができる。 The second shaft 44 of this embodiment is a solid shaft. Therefore, the fluid O accumulated in the hollow portion 21H of the first shaft 21 does not flow into the inside of the second shaft 44. According to this embodiment, the fluid O accumulated in the hollow part 21H can be easily guided to the other axial side of the hollow part 21H, and the motor 2 can be cooled and the third bearing 5C can be suitably lubricated.
　第３流路５２ｄは、第２ベアリング５Ｂの内輪５Ｂｃと外輪５Ｂａとの間に設けられる流路である。すなわち、第３流路５２ｄは、第２ベアリング５Ｂを含む流路である。本実施形態によれば、第３流路５２ｄに流体Ｏが流れることで、第２ベアリング５Ｂが潤滑される。 The third flow path 52d is a flow path provided between the inner ring 5Bc and outer ring 5Ba of the second bearing 5B. That is, the third flow path 52d is a flow path that includes the second bearing 5B. According to this embodiment, the second bearing 5B is lubricated by the fluid O flowing through the third flow path 52d.
　本実施形態の連結空間Ａは、第１流路５２ａを介して第１貯留部８４に繋がる。連結空間Ａには、第１貯留部８４から安定的に流体Ｏが供給される。本実施形態によれば、連結空間Ａが、第２流路５２ｅ、および第３流路５２ｄに流体Ｏを安定的に供給することができ、第２流路５２ｅにおいて連結部３を潤滑させ、第３流路５２ｄにおいて第２ベアリング５Ｂを潤滑させることができる。 The connection space A of this embodiment is connected to the first storage section 84 via the first flow path 52a. The fluid O is stably supplied to the connection space A from the first storage section 84. According to this embodiment, the connection space A can stably supply the fluid O to the second flow path 52e and the third flow path 52d, and lubricate the connection portion 3 in the second flow path 52e. The second bearing 5B can be lubricated in the third flow path 52d.
　本実施形態の第２ベアリング５Ｂは、動力伝達部４の第２シャフト４４を支持する。このため、第２ベアリング５Ｂは、第１ベアリング５Ａと比較して、ギヤ同士の噛み合いに起因する振動が伝わり易い。本実施形態によれば、第２ベアリング５Ｂの外輪５Ｂａと内輪５Ｂｃとの間に第３流路５２ｄを設けて第２ベアリング５Ｂを潤滑することで、第２ベアリング５Ｂの動作を安定させることができる。 The second bearing 5B of this embodiment supports the second shaft 44 of the power transmission section 4. Therefore, vibrations caused by the meshing of the gears are more easily transmitted to the second bearing 5B than to the first bearing 5A. According to this embodiment, the operation of the second bearing 5B can be stabilized by providing the third flow path 52d between the outer ring 5Ba and the inner ring 5Bc of the second bearing 5B to lubricate the second bearing 5B. can.
　本実施形態において、第１ベアリング５Ａ、および第２ベアリング５Ｂは、ボールベアリングである。第１ベアリング５Ａ、および第２ベアリング５Ｂは、それぞれ球状の転動体５Ａｂ、５Ｂｂを有する。本実施形態において、第２ベアリング５Ｂの転動体５Ｂｂの直径は、第１ベアリング５Ａの転動体５Ａｂの直径より大きい。本実施形態によれば、動力伝達部４からの振動を受け易い第２ベアリング５Ｂの強度および剛性を高めて、動力伝達部４の動作を円滑にすることができる。また、第１ギヤ４１および第２ギヤ４２としてヘリカルギヤを採用する場合、動力伝達部４の駆動時に第２ベアリング５Ｂには、軸方向の力が付与される。第２ベアリング５Ｂは、転動体５Ｂｂを大きくすることで第２シャフト４４に付与される軸方向の力に対し第２シャフト４４を安定して支持できる。 In this embodiment, the first bearing 5A and the second bearing 5B are ball bearings. The first bearing 5A and the second bearing 5B have spherical rolling elements 5Ab and 5Bb, respectively. In this embodiment, the diameter of the rolling elements 5Bb of the second bearing 5B is larger than the diameter of the rolling elements 5Ab of the first bearing 5A. According to this embodiment, the strength and rigidity of the second bearing 5B, which is susceptible to vibrations from the power transmission section 4, can be increased, and the operation of the power transmission section 4 can be made smooth. Further, when helical gears are used as the first gear 41 and the second gear 42, an axial force is applied to the second bearing 5B when the power transmission section 4 is driven. The second bearing 5B can stably support the second shaft 44 against the axial force applied to the second shaft 44 by increasing the size of the rolling elements 5Bb.
　なお、第１ベアリング５Ａ、および第２ベアリング５Ｂは、円柱状の転動体５Ａｂ、５Ｂｂを有するころ軸受であってもよい。この場合においても、球状又は円柱状の転動体５Ａｂ、５Ｂｂの直径を比較して、第１ベアリング５Ａの方が大きければ上述の効果得ることができる。 Note that the first bearing 5A and the second bearing 5B may be roller bearings having cylindrical rolling elements 5Ab and 5Bb. Even in this case, the above-mentioned effect can be obtained if the diameters of the spherical or cylindrical rolling elements 5Ab and 5Bb are compared and the first bearing 5A is larger.
　本実施形態では、連結開口部２１ａが第１シャフト２１に設けられ、連結凸部４４ａが第２シャフト４４に設ける。連結凸部４４ａと連結開口部２１ａとは互いに嵌合するため、連結凸部４４ａが設けられるシャフトは、凹部が設けられるシャフトと比較して直径が大きくなる。本実施形態によれば、第１シャフト２１に連結開口部２１ａを設け第２シャフト４４に連結凸部４４ａを設けることで、第２シャフト４４を第１シャフト２１よりも小径にすることができる。このため、第２シャフト４４を支持する第２ベアリング５Ｂの転動体５Ｂｂを大型化しても、第２ベアリング５Ｂの外径が大きくなりすぎることを抑制できる。第２ベアリング５Ｂは、隔壁６５ａにおいて第３シャフト４５を支持する第５ベアリング５Ｅ（図１参照）と隣り合って支持される。第２ベアリング５Ｂが大型化すると、第２ベアリング５Ｂと第５ベアリング５Ｅとの収容スペースを確保するために、第２シャフト４４と第３シャフト４５とを離間させる必要が生じる。これに伴いギヤ室Ｒ２の体積を大きくする必要が生じ、ひいてはハウジング６の大型化に繋がる。本実施形態によれば、第２ベアリング５Ｂの外径が大きくなりすぎることを抑制することで、第２シャフト４４と第３シャフト４５とを近づけて配置できる。これにより、ハウジング６の大型化を抑制できる。 In this embodiment, the connecting opening 21a is provided on the first shaft 21, and the connecting convex portion 44a is provided on the second shaft 44. Since the connecting protrusion 44a and the connecting opening 21a fit into each other, the shaft provided with the connecting protrusion 44a has a larger diameter than the shaft provided with the recess. According to this embodiment, the second shaft 44 can be made smaller in diameter than the first shaft 21 by providing the first shaft 21 with the connecting opening 21a and the second shaft 44 with the connecting convex portion 44a. Therefore, even if the rolling elements 5Bb of the second bearing 5B that supports the second shaft 44 are increased in size, the outer diameter of the second bearing 5B can be prevented from becoming too large. The second bearing 5B is supported adjacent to the fifth bearing 5E (see FIG. 1) that supports the third shaft 45 on the partition wall 65a. When the second bearing 5B becomes larger, it becomes necessary to separate the second shaft 44 and the third shaft 45 in order to secure the accommodation space for the second bearing 5B and the fifth bearing 5E. Accordingly, it becomes necessary to increase the volume of the gear chamber R2, which in turn leads to an increase in the size of the housing 6. According to this embodiment, the second shaft 44 and the third shaft 45 can be disposed close to each other by preventing the outer diameter of the second bearing 5B from becoming too large. Thereby, it is possible to suppress the housing 6 from increasing in size.
　（第２実施形態）
　図７は、第２実施形態の駆動装置１０１の連結部３を示す断面図である。なお、上述の実施形態と同一態様の構成要素については、同一符号を付し、その説明を省略する。 (Second embodiment)
FIG. 7 is a sectional view showing the connecting portion 3 of the drive device 101 of the second embodiment. Note that the same reference numerals are given to the same components as in the above-described embodiment, and the explanation thereof will be omitted.
　本実施形態の駆動装置１０１は、上述の実施形態と同様に、第１シャフト１２１を有するモータ２（図７で省略）、第２シャフト４４を有する動力伝達部４（図７で省略）、ハウジング１０６、第１ベアリング５Ａ、第２ベアリング５Ｂ、および第２供給流路１５２を有する。ハウジング１０６は、モータ室Ｒ１とギヤ室Ｒ２とを区画する隔壁６５ａを有する。また、隔壁６５ａには、モータ室Ｒ１とギヤ室Ｒ２とを連通する連通孔６５ｈが設けられる。隔壁６５ａは、連通孔６５ｈの内縁に沿ってギヤ室Ｒ２側（すなわち、軸方向一方側（－Ｙ側））に突出する筒部１１１を有する。連通孔６５ｈの内周面は、第１ベアリング５Ａ、第２ベアリング５Ｂ、およびシール部材１０５Ｓを保持する。 Similarly to the embodiments described above, the drive device 101 of this embodiment includes a motor 2 having a first shaft 121 (omitted in FIG. 7), a power transmission section 4 having a second shaft 44 (omitted in FIG. 7), and a housing. 106, a first bearing 5A, a second bearing 5B, and a second supply channel 152. The housing 106 has a partition wall 65a that partitions the motor chamber R1 and the gear chamber R2. Further, the partition wall 65a is provided with a communication hole 65h that communicates the motor chamber R1 and the gear chamber R2. The partition wall 65a has a cylindrical portion 111 that protrudes toward the gear chamber R2 (ie, one axial side (-Y side)) along the inner edge of the communication hole 65h. The inner peripheral surface of the communication hole 65h holds the first bearing 5A, the second bearing 5B, and the seal member 105S.
　本実施形態の第１シャフト１２１、および第２シャフト４４は、ともに中実のシャフトである。第１シャフト１２１の軸方向一方側（－Ｙ側）の端部は、連結開口部１２１ａを有する。本実施形態の連結開口部１２１ａは、凹状である。連結開口部１２１ａの内周面には、複数のスプライン溝２１ｓが設けられる。連結開口部１２１ａには、第２シャフト４４の連結凸部４４ａが挿入される。連結開口部１２１ａのスプライン溝２１ｓと連結凸部４４ａのスプライン突起４４ｓとは、互いに嵌合して連結部３を構成する。 The first shaft 121 and the second shaft 44 of this embodiment are both solid shafts. The first shaft 121 has a connecting opening 121a at one axial end (-Y side). The connection opening 121a of this embodiment has a concave shape. A plurality of spline grooves 21s are provided on the inner peripheral surface of the connection opening 121a. The connecting convex portion 44a of the second shaft 44 is inserted into the connecting opening 121a. The spline groove 21s of the connection opening 121a and the spline protrusion 44s of the connection convex part 44a fit together to form the connection part 3.
　本実施形態において、連結開口部１２１ａの底面１２１ｂと、連結凸部４４ａの先端面４４ｂとの間には、軸方向の隙間が設けられる。以下の説明において、底面１２１ｂと先端面４４ｂとの間の隙間を第３貯留部Ｂと呼ぶ。すなわち、底面１２１ｂと先端面４４ｂとの間には、第３貯留部Ｂが設けられる。第３貯留部Ｂは、連結開口部１２１ａの内周面によって径方向外側から囲まれ、底面１２１ｂと先端面４４ｂとによって軸方向に挟まれる空間である。第３貯留部Ｂには、流体Ｏが留まる。 In this embodiment, an axial gap is provided between the bottom surface 121b of the connection opening 121a and the tip surface 44b of the connection convex portion 44a. In the following description, the gap between the bottom surface 121b and the tip surface 44b will be referred to as a third storage section B. That is, the third reservoir B is provided between the bottom surface 121b and the tip surface 44b. The third storage portion B is a space surrounded from the outside in the radial direction by the inner circumferential surface of the connection opening 121a, and sandwiched in the axial direction by the bottom surface 121b and the tip surface 44b. The fluid O remains in the third reservoir B.
　連通孔６５ｈにおける第１ベアリング５Ａと第２ベアリング５Ｂの軸方向の間には、連結空間Ａが設けられる。連結空間Ａには、連結開口部１２１ａが開口する。また、連通孔６５ｈには、シール部材１０５Ｓが設けられる。本実施形態の筒部１１１は、第２ベアリング５Ｂに対してさらに軸方向一方側（－Ｙ側）に延びる。シール部材１０５Ｓは、第２ベアリング５Ｂの軸方向一方側（－Ｙ側）で筒部１１１の内周面に固定される。すなわち、シール部材１０５Ｓは、第１ベアリング５Ａ、および第２ベアリング５Ｂよりも軸方向一方側（－Ｙ側）に配置される。このため、連結空間Ａに流入した流体Ｏを第１ベアリング５Ａおよび第２ベアリング５Ｂに供給することができ、第１ベアリング５Ａおよび第２ベアリング５Ｂを好適に潤滑できる。さらに、シール部材１０５Ｓは、連結空間Ａに流入する流体Ｏが、ギヤ室Ｒ２側に流出することを抑制することができる。シール部材１０５Ｓが連結空間Ａに流体Ｏを留めることで、多くの流体Ｏを連結部３、第１ベアリング５Ａおよび第２ベアリング５Ｂに供給できる。 A connection space A is provided between the first bearing 5A and the second bearing 5B in the axial direction in the communication hole 65h. A connection opening 121a opens in the connection space A. Further, a seal member 105S is provided in the communication hole 65h. The cylindrical portion 111 of this embodiment further extends to one side (-Y side) in the axial direction with respect to the second bearing 5B. The seal member 105S is fixed to the inner peripheral surface of the cylindrical portion 111 on one axial side (-Y side) of the second bearing 5B. That is, the seal member 105S is arranged on one side in the axial direction (-Y side) of the first bearing 5A and the second bearing 5B. Therefore, the fluid O that has flowed into the connection space A can be supplied to the first bearing 5A and the second bearing 5B, and the first bearing 5A and the second bearing 5B can be suitably lubricated. Furthermore, the seal member 105S can suppress the fluid O flowing into the connection space A from flowing out to the gear chamber R2 side. Since the seal member 105S retains the fluid O in the connection space A, a large amount of the fluid O can be supplied to the connection portion 3, the first bearing 5A, and the second bearing 5B.
　第２供給流路（流路）１５２は、第１流路５２ａと第２流路１５２ｂと流入流路１５２ｃと流出流路１５２ｄとを有する。第１流路５２ａは、ギヤ室Ｒ２と連結空間Ａとを繋ぐ。第２流路１５２ｂは、連結空間Ａとモータ室Ｒ１とを繋ぐ。流入流路１５２ｃ、および流出流路１５２ｄは、ともに連結空間Ａと第３貯留部Ｂとを繋ぐ流路である。第１流路５２ａは、第１実施形態と同様の構成を有する。 The second supply channel (channel) 152 has a first channel 52a, a second channel 152b, an inflow channel 152c, and an outflow channel 152d. The first flow path 52a connects the gear chamber R2 and the connection space A. The second flow path 152b connects the connection space A and the motor chamber R1. Both the inflow channel 152c and the outflow channel 152d are channels that connect the connection space A and the third storage section B. The first flow path 52a has the same configuration as the first embodiment.
　第２流路１５２ｂは、第１ベアリング５Ａの内輪５Ａｃと外輪５Ａａとの間に設けられる流路である。すなわち、第２流路１５２ｂは、第１ベアリング５Ａを含む流路である。本実施形態によれば、第２流路１５２ｂに流体Ｏが流れることで、第１ベアリング５Ａが潤滑される。 The second flow path 152b is a flow path provided between the inner ring 5Ac and outer ring 5Aa of the first bearing 5A. That is, the second flow path 152b is a flow path that includes the first bearing 5A. According to this embodiment, the first bearing 5A is lubricated by the fluid O flowing through the second flow path 152b.
　流入流路１５２ｃは、連結空間Ａから第３貯留部Ｂに向かって流体Ｏを流す経路である。一方で、流出流路１５２ｄは、第３貯留部Ｂから連結空間Ａに向かって流体Ｏを流す経路である。流入流路１５２ｃ、および流出流路１５２ｄは、ともにスプライン溝２１ｓとスプライン突起４４ｓとの間を通る。 The inflow channel 152c is a path through which the fluid O flows from the connection space A toward the third storage section B. On the other hand, the outflow channel 152d is a path through which the fluid O flows from the third storage section B toward the connection space A. Both the inflow channel 152c and the outflow channel 152d pass between the spline groove 21s and the spline protrusion 44s.
　本実施形態の第２供給流路１５２によれば、第１流路５２ａと第２流路１５２ｂとが連結空間Ａにおいて接続される。すなわち、第２供給流路１５２は、第１流路５２ａと第２流路１５２ｂとの接続部で、連結空間Ａを通過するように設けられる。このため、連結空間Ａから連結部３に流体Ｏを供給しつつ、第１流路５２ａおよび第２流路１５２ｂによってモータ室Ｒ１とギヤ室Ｒ２との間で流体Ｏを移動させることができる。なお、図７においては、第１流路５２ａと第２流路１５２ｂとの間に、流入流路１５２ｃと流出流路１５２ｄと介在するように見える。しかしながら、連結空間Ａは、中心軸線Ｊ１を中心として周方向に延びる円環状の空間であり、第１流路５２ａと第２流路１５２ｂとは直接的に繋がっている。 According to the second supply flow path 152 of this embodiment, the first flow path 52a and the second flow path 152b are connected in the connection space A. That is, the second supply flow path 152 is provided so as to pass through the connection space A at the connection portion between the first flow path 52a and the second flow path 152b. Therefore, while supplying the fluid O from the connection space A to the connection part 3, the fluid O can be moved between the motor chamber R1 and the gear chamber R2 through the first flow path 52a and the second flow path 152b. In addition, in FIG. 7, it appears that an inflow channel 152c and an outflow channel 152d are interposed between the first channel 52a and the second channel 152b. However, the connection space A is an annular space extending in the circumferential direction centering on the central axis J1, and the first flow path 52a and the second flow path 152b are directly connected.
　以上に、本発明の様々な実施形態および変形例を説明したが、各実施形態および変形例における各構成およびそれらの組み合わせ等は一例であり、本発明の趣旨から逸脱しない範囲内で、構成の付加、省略、置換およびその他の変更が可能である。また、本発明は実施形態によって限定されることはない。 Various embodiments and modifications of the present invention have been described above, but each configuration and combination thereof in each embodiment and modification is merely an example, and the configurations may be changed without departing from the spirit of the present invention. Additions, omissions, substitutions, and other changes are possible. Moreover, the present invention is not limited by the embodiments.
１，１０１…駆動装置、２…モータ、４…動力伝達部、５Ａ…第１ベアリング、５Ｂ…第２ベアリング、５Ｓ，１０５Ｓ，２０５Ｓ…シール部材、６，１０６…ハウジング、１１，１１１…筒部、１１ａ…第１凹溝（凹溝）、１１ｃ，１２１ｂ…底面、２０…ロータ、２１，１２１…第１シャフト（シャフト）、２１ａ，１２１ａ…連結開口部、２１ｓ…スプライン溝、２１Ｈ…中空部（内部）、３０…ステータ、４１、４２、４３、４６ｇ…ギヤ、４４…第２シャフト（シャフト）、４４ａ…連結凸部、４４ｓ…スプライン突起、５２，１５２…第２供給流路（流路）、５２ａ，２５２ａ…第１流路、５２ｅ，１５２ｂ…第２流路、６５ａ…隔壁、６５ｈ…連通孔、８４…第１貯留部（キャッチタンク）、８４ａ…孔部、Ａ…連結空間、Ｊ１…中心軸線、Ｏ…流体、Ｒ１，Ｒ２…ギヤ室、Ｒ１…モータ室 DESCRIPTION OF SYMBOLS 1,101... Drive device, 2... Motor, 4... Power transmission part, 5A... First bearing, 5B... Second bearing, 5S, 105S, 205S... Seal member, 6,106... Housing, 11,111... Cylinder part , 11a...First groove (concave groove), 11c, 121b...Bottom surface, 20...Rotor, 21, 121...First shaft (shaft), 21a, 121a...Connection opening, 21s...Spline groove, 21H...Hollow part (Inside), 30... Stator, 41, 42, 43, 46g... Gear, 44... Second shaft (shaft), 44a... Connection convex portion, 44s... Spline protrusion, 52, 152... Second supply channel (channel ), 52a, 252a...first flow path, 52e, 152b...second flow path, 65a...partition wall, 65h...communication hole, 84...first storage part (catch tank), 84a...hole, A...connection space, J1...Center axis, O...Fluid, R1, R2...Gear chamber, R1...Motor chamber

Claims (13)

  1. 　中心軸線を中心として回転する第１シャフトを有するロータ、および前記ロータを囲むステータを有するモータと、
    　複数のギヤ、および前記中心軸線を中心として回転する第２シャフトを有し、前記モータの動力を伝達する動力伝達部と、
    　前記モータを収容するモータ室と前記動力伝達部を収容するギヤ室とが内部に設けられるハウジングと、
    　前記第１シャフトを支持する第１ベアリングと、
    　前記第２シャフトを支持する第２ベアリングと、
    　流体が流れる流路と、を備え、
    　前記第１シャフトの軸方向一方側の端部は、内周面に軸方向に延びる複数のスプライン溝が設けられる連結開口部を有し、
    　前記第２シャフトの軸方向他方側の端部は、外周面に軸方向に延びる複数のスプライン突起が設けられる連結凸部を有し、
    　前記第１シャフトと前記第２シャフトとは、前記連結開口部の前記スプライン溝と前記連結凸部の前記スプライン突起との噛み合いにより互いに連結され、
    　前記ハウジングは、前記モータ室と前記ギヤ室とを区画する隔壁を有し、
    　前記隔壁には、前記モータ室と前記ギヤ室とを連通する連通孔が設けられ、
    　前記連通孔の内周面は、前記第１ベアリングおよび前記第２ベアリングを保持し、
    　前記連通孔における前記第１ベアリングと前記第２ベアリングの軸方向の間には、前記連結開口部が開口する連結空間が設けられ、
    　前記流路は、
    　　前記ギヤ室と前記連結空間とを繋ぐ第１流路と、
    　　前記連結空間と前記モータ室とを繋ぐ第２流路と、を有する、駆動装置。     a motor having a rotor having a first shaft rotating about a central axis and a stator surrounding the rotor;
    a power transmission section that has a plurality of gears and a second shaft that rotates around the central axis, and that transmits the power of the motor;
    a housing in which a motor chamber for accommodating the motor and a gear chamber for accommodating the power transmission section;
    a first bearing that supports the first shaft;
    a second bearing that supports the second shaft;
    A channel through which fluid flows,
    One end of the first shaft in the axial direction has a connecting opening in which a plurality of spline grooves extending in the axial direction are provided on the inner circumferential surface,
    The other end of the second shaft in the axial direction has a connecting convex portion provided with a plurality of spline protrusions extending in the axial direction on the outer peripheral surface,
    The first shaft and the second shaft are connected to each other by engagement between the spline groove of the connection opening and the spline protrusion of the connection convex portion,
    The housing has a partition wall that partitions the motor chamber and the gear chamber,
    The partition wall is provided with a communication hole that communicates the motor chamber and the gear chamber,
    The inner peripheral surface of the communication hole holds the first bearing and the second bearing,
    A connection space in which the connection opening opens is provided between the first bearing and the second bearing in the communication hole in the axial direction,
    The flow path is
    a first flow path connecting the gear chamber and the connection space;
    A drive device comprising: a second flow path connecting the connection space and the motor chamber.
  2. 　前記第１シャフトは、筒状の中空シャフトであり、
    　前記第２流路は、前記連結空間と前記第１シャフトの内部とを繋ぐ、請求項１に記載の駆動装置。     The first shaft is a cylindrical hollow shaft,
    The drive device according to claim 1, wherein the second flow path connects the connection space and the inside of the first shaft.
  3. 　前記第２シャフトは、中実のシャフトである、請求項２に記載の駆動装置。 The drive device according to claim 2, wherein the second shaft is a solid shaft.
  4. 　前記連通孔には、前記連通孔の内周面と前記第１シャフトの外周面との間の隙間を封止するシール部材が設けられる、請求項２又は３に記載の駆動装置。 The drive device according to claim 2 or 3, wherein the communication hole is provided with a seal member that seals a gap between an inner peripheral surface of the communication hole and an outer peripheral surface of the first shaft.
  5. 　前記シール部材は、前記第１ベアリングと前記第２ベアリングとの軸方向の間に位置し、
    　前記連結空間は、前記シール部材と前記第２ベアリングとの軸方向の間に設けられる、請求項４に記載の駆動装置。     The sealing member is located between the first bearing and the second bearing in the axial direction,
    The drive device according to claim 4, wherein the connection space is provided between the seal member and the second bearing in the axial direction.
  6. 　前記シール部材は、前記第１ベアリング、および前記第２ベアリングよりも軸方向他方側に配置される、請求項４に記載の駆動装置。 The drive device according to claim 4, wherein the seal member is arranged on the other axial side of the first bearing and the second bearing.
  7. 　前記シール部材は、前記連通孔の内周面に保持され、前記第１シャフトの外周面に接触し、
    　前記第１シャフトは、前記シール部材と接触する部分の外径が、前記第１ベアリングに支持される部分の外径より小さい、請求項４～６の何れか一項に記載の駆動装置。     The sealing member is held on the inner circumferential surface of the communication hole and contacts the outer circumferential surface of the first shaft,
    7. The drive device according to claim 4, wherein the first shaft has an outer diameter smaller in a portion that contacts the seal member than in a portion supported by the first bearing.
  8. 　前記第２流路は、前記第１ベアリングを含む流路である、請求項１に記載の駆動装置。 The drive device according to claim 1, wherein the second flow path is a flow path that includes the first bearing.
  9. 　前記連通孔には、前記連通孔の内周面と前記第２シャフトの外周面との間の隙間を封止するシール部材が設けられる、請求項８に記載の駆動装置。 The drive device according to claim 8, wherein the communication hole is provided with a sealing member that seals a gap between an inner peripheral surface of the communication hole and an outer peripheral surface of the second shaft.
  10. 　前記隔壁は、前記連通孔の内縁に沿って前記第２ベアリングを囲み保持する筒部を有し、
    　筒部には、径方向に延びる孔部が設けられ、
    　前記孔部は、前記第１流路の一部を構成する、請求項１～９の何れか一項に記載の駆動装置。     The partition wall has a cylindrical portion that surrounds and holds the second bearing along an inner edge of the communication hole,
    The cylindrical portion is provided with a hole extending in the radial direction,
    The drive device according to any one of claims 1 to 9, wherein the hole constitutes a part of the first flow path.
  11. 　前記筒部の内周面には、軸方向に沿って延びる凹溝が設けられ、
    　前記孔部は、前記凹溝の底面に開口する、請求項１０に記載の駆動装置。     A concave groove extending along the axial direction is provided on the inner circumferential surface of the cylindrical portion,
    The drive device according to claim 10, wherein the hole opens at a bottom surface of the groove.
  12. 　前記ギヤ室には、上側に開口するキャッチタンクが配置され、
    　前記孔部は、前記キャッチタンクと前記筒部の内周面とを繋ぐ、請求項１０又は１１に記載の駆動装置。     A catch tank that opens upward is arranged in the gear chamber,
    The drive device according to claim 10 or 11, wherein the hole connects the catch tank and the inner peripheral surface of the cylindrical portion.
  13. 　前記第１流路は、前記第２ベアリングを含む流路である、請求項１～１２の何れか一項に記載の駆動装置。 The drive device according to any one of claims 1 to 12, wherein the first flow path is a flow path that includes the second bearing.
PCT/JP2022/047298 2022-03-31 2022-12-22 Drive device WO2023188621A1 (en)

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001190042A (en) * 1999-12-28 2001-07-10 Honda Motor Co Ltd Lubricating structure for rotor bearing of electric motor
JP2007205467A (en) * 2006-02-01 2007-08-16 Honda Motor Co Ltd Power transmission device for vehicle
JP2019108932A (en) * 2017-12-18 2019-07-04 トヨタ自動車株式会社 Vehicle drive device
JP2021148194A (en) * 2020-03-18 2021-09-27 トヨタ自動車株式会社 Oil supply device
JP2021162079A (en) * 2020-03-31 2021-10-11 日本電産株式会社 Driving device

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001190042A (en) * 1999-12-28 2001-07-10 Honda Motor Co Ltd Lubricating structure for rotor bearing of electric motor
JP2007205467A (en) * 2006-02-01 2007-08-16 Honda Motor Co Ltd Power transmission device for vehicle
JP2019108932A (en) * 2017-12-18 2019-07-04 トヨタ自動車株式会社 Vehicle drive device
JP2021148194A (en) * 2020-03-18 2021-09-27 トヨタ自動車株式会社 Oil supply device
JP2021162079A (en) * 2020-03-31 2021-10-11 日本電産株式会社 Driving device

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