JP2020020462A - Vehicular drive unit - Google Patents

Abstract

To provide a vehicular drive unit suppressing a loss of driving force that is transmitted from a driving force source to wheels when an oil pump is driven.SOLUTION: In an insertion part 48b of a pump drive shaft 48, a first spiral groove 48i and a second spiral groove 48j are formed for generating thrust force FS during rotation of the pump drive shaft 48. Accordingly, when an oil pump 22 is driven, the pump drive shaft 48 is moved relatively to a second case member 42 toward the opposite side to an inner rotor 50 side in a third rotation axis C3 direction by the thrust force FS generated by the first spiral groove 48i and the second spiral groove 48j which are formed in the insertion part 48b, and a flange 48f of the pump drive shaft 48 becomes hard to come into contact with a cylindrical protrusion 42h formed on the second case member 42, so that it is possible to suppress a loss of driving force transmitted from an electric motor 12 to drive wheels 14L, 14R when the oil pump 22 is driven.SELECTED DRAWING: Figure 5

Description

  The present invention provides a power transmission mechanism that transmits a driving force from a driving power source to wheels, and a pump rotor that is rotationally driven by a pump drive shaft that is connected to a rotation shaft provided in the power transmission mechanism, to thereby supply oil. The present invention relates to a technique for a vehicle drive device including an oil pump that discharges, and capable of suitably suppressing a loss of a driving force transmitted from the driving force source to the wheels when the oil pump is driven.

  (A) a power transmission mechanism for transmitting a driving force from a driving force source to wheels, (b) a case accommodating the power transmission mechanism, and (c) provided in the power transmission mechanism so as to be rotatable by the case. A pump having a pump shaft housed in a pump chamber formed by a supported rotating shaft and (d) the case and a pump cover attached to the case, wherein the pump rotor is connected to the rotating shaft 2. Description of the Related Art A vehicular drive device including an oil pump that discharges oil by being rotationally driven by a drive shaft is known. For example, this is a vehicle drive device described in Patent Document 1.

JP 2013-119918 A

  By the way, in the vehicle drive device as described above, in connecting the pump drive shaft to the pump rotor so as to be able to transmit power, the pump drive shaft has an insertion portion that is inserted through an insertion hole formed in the case. A fitting portion fitted to one end side of the pump drive shaft in the axial direction relative to the insertion portion, that is, to the pump rotor side in the axial direction so as to be able to transmit power to the pump rotor and to be relatively movable in the axial direction. It is conceivable to provide However, if an excessive load acts on the case or the pump rotor relative to the case or the pump rotor from the pump drive shaft toward one end in the axial direction, for example, during assembly, the fitting portion and the insertion portion There is a problem that a step formed between the pump rotor and the pump abuts on the pump rotor and an excessive load is input to the pump rotor.

  On the other hand, when the pump drive shaft is moved relative to the case toward the one end side in the axial direction with respect to the case, the pump drive shaft is moved before the step portion comes into contact with the pump rotor. It is conceivable to provide a large-diameter flange portion that protrudes to the outer peripheral side in order to regulate the relative movement of the pump drive shaft in contact with the case. However, in this case, when the vehicle travels, the flange of the pump drive shaft, which is a rotating member, comes into contact with the case, which is a non-rotating member, and sliding friction occurs between the flange and the case. Therefore, there is a possibility that a loss occurs in the driving force transmitted from the driving force source to the wheels when the pump drive shaft rotates, that is, when the oil pump is driven.

  The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a vehicle drive device that suppresses a loss of drive force transmitted from a drive force source to wheels when an oil pump is driven. Is to provide.

  The gist of the first invention is as follows: (a) a power transmission mechanism for transmitting a driving force from a driving force source to wheels, a case accommodating the power transmission mechanism, and a case provided in the power transmission mechanism, A rotating shaft rotatably supported on the pump case, and a pump rotor housed in a pump chamber formed by the case and a pump cover attached to the case. The pump rotor is connected to the rotating shaft. An oil pump that discharges oil by being rotationally driven by a pump drive shaft, wherein (b) the pump drive shaft is inserted through an insertion hole formed in the case. And (c) provided at one end side in the axial direction with respect to the insertion portion, so as to be able to transmit power to the pump rotor and to be movable relative to the pump rotor in the axial direction. A first fitting portion fitted to the core, (d) a step portion formed between the first fitting portion and the insertion portion, and (e) another end in the axial direction of the insertion portion. A second fitting portion provided on the side of the first portion, the second fitting portion being capable of transmitting power to the rotating shaft and being concentrically fitted to the rotating shaft so as to be relatively movable in the axial direction; and (f) the second fitting portion. When the pump drive shaft is provided between the insertion portion and the pump drive shaft is relatively moved toward the one end in the axial direction with respect to the case, the case before the stepped portion contacts the pump rotor. And a flange portion having a diameter larger than that of the insertion portion, which restricts relative movement of the pump drive shaft, and (g) the insertion portion includes: A screw for generating a thrust force toward the other axial end of the pump drive shaft with respect to the case. In that the grooves are formed.

  According to the first invention, the insertion portion is formed with a spiral groove for generating a thrust force toward the other end in the axial direction with respect to the case when the pump drive shaft rotates. Have been. For this reason, when the pump drive shaft rotates, that is, when the oil pump is driven, the thrust force generated by the spiral groove formed in the insertion portion causes the pump drive shaft to move relative to the case in the axial direction. The driving force transmitted from the driving force source to the wheels at the time of driving the oil pump since the flange portion of the pump driving shaft is less likely to contact the case by being relatively moved toward the end side. Loss can be suppressed suitably.

1 is a sectional view schematically illustrating a configuration of an electric vehicle to which the present invention is suitably applied. It is sectional drawing which shows a part of FIG. 1 in detail. FIG. 3 is an enlarged view in which a peripheral portion of an oil pump in FIG. 2 is enlarged. FIG. 4 is a sectional view taken along line IV-IV of FIG. 3. FIG. 4 is a diagram for explaining a first spiral groove and a second spiral groove formed in an insertion portion of a pump drive shaft provided in the oil pump of FIG. 3.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. In the following examples, the drawings are simplified or modified as appropriate, and the dimensional ratios, shapes, and the like of the respective parts are not necessarily drawn accurately.

  FIG. 1 is a sectional view schematically illustrating a configuration of an electric vehicle 10 to which the present invention is suitably applied. The electric vehicle 10 includes a driving device (vehicle driving device) 16 that drives a pair of left and right driving wheels (wheels) 14L and 14R by an electric motor 12 that is a driving force source for traveling. As shown in FIG. 1, the driving device 16 includes an electric motor 12, a power transmission mechanism 18 for transmitting a driving force from the electric motor 12 to a pair of left and right driving wheels 14 </ b> L, 14 </ b> R, an electric motor 12 and a power transmission mechanism. An accommodation case (case) 20 for accommodating 18 and the like, a mechanical oil pump 22 driven by the electric motor 12, and drive shafts 24L and 24R rotating together with the drive wheels 14L and 14R are provided. The power transmission mechanism 18 includes a gear mechanism 26 connected to the electric motor 12 so as to transmit power, and a differential device 28 connected to the gear mechanism 26 so as to transmit power.

  As shown in FIGS. 1 and 2, the gear mechanism 26 has a cylindrical first rotating shaft 26 a connected to a rotor shaft 30 provided on the electric motor 12 so as to transmit power, and is integrated with the first rotating shaft 26 a. Gear 26c meshing with a ring gear 28r provided in the differential device 28, and a large-diameter gear having a larger diameter than the small-diameter gear 26c and meshing with a pinion 26b formed on the first rotating shaft 26a. 26d, and a cylindrical second rotating shaft (rotating shaft) 26e in which the small-diameter gear 26c and the large-diameter gear 26d are integrally fixed. In the gear mechanism 26, the second rotation shaft 26e rotates around the third rotation axis C3 in the housing case 20 via a pair of first bearings 32 and 34 provided at both ends of the second rotation shaft 26e. Supported as possible. The first bearings 32 and 34 are tapered roller bearings as shown in FIG. The first rotating shaft 26a is rotatable around the first rotating axis C1 in the housing case 20 via a pair of second bearings 36 and 38 provided at both ends of the first rotating shaft 26a, ie, the electric motor. The rotor 12 is rotatably supported around the same rotation axis C1 as the rotor shaft 30. The pinion 26b and the large-diameter gear 26d are bevel gears. The ring gear 28r of the differential device 28 is rotatably supported around a second rotation axis C2 (see FIG. 1).

  As shown in FIGS. 1 and 2, the housing case 20 includes a first case member 40, a second case member 42 integrally fixed to the first case member 40 by a first fastening bolt Bo <b> 1, A third case member 44 integrally fixed to the member 40 by a second fastening bolt Bo2. Further, the housing case 20 includes a first housing space S1 formed by the first case member 40 and the second case member 42, and a second housing space formed by the first case member 40 and the third case member 44. A space S2 is formed, and the first housing space S1 houses the power transmission mechanism 18 and the like, that is, the gear mechanism 26, the differential device 28, and the like, and the second housing space S2 houses the electric motor 12 and the like. ing. The first case member 40 has a partition wall 40a separating the first storage space S1 and the second storage space S2, and the second case member 42 has a partition wall formed in the first case member 40. A wall 42a facing the 40a is formed.

  As shown in FIGS. 2 to 4, the oil pump 22 is an internal gear type oil pump. The oil pump 22 includes a wall 42 a of the second case member 42 and a wall 42 a of the second case member 42. A pump chamber S3 formed by a pump cover 46 attached to the pump shaft 46 and a pump drive shaft 48 having a plurality of outer teeth 50a and connected to the second rotation shaft 26e so as to be rotatable about the third rotation axis C3. A third rotational axis is formed by a formed annular inner rotor (pump rotor) 50 and a plurality of inner peripheral teeth 52a meshing with outer peripheral teeth 50a of the inner rotor 50 and a concave portion 42b formed in a wall portion 42a of the second case member 42. An annular outer rotor 52 rotatably supported around a fourth rotation axis C4 (see FIG. 4) eccentric from C3. FIG. 4 is a sectional view taken along line IV-IV of FIG. 3, and FIG. 3 is a sectional view taken along line AA of FIG.

  As shown in FIGS. 2 and 3, a sliding surface of the pump cover 46 between the inner rotor 50 and the outer rotor 52 has a suction-side connection port 46a connected to a suction oil passage (not shown) for sucking oil. For example, a first pumping-side connection port 46b for pumping oil to an axial oil passage 48a formed in the pump drive shaft 48 and the like is formed. The pump cover 46 is provided with a first oil supply oil passage 46c for supplying the oil pumped from the oil pump 22 to the first pumping-side connection port 46b to an axial oil passage 48a formed in the pump drive shaft 48. Have been.

  As shown in FIGS. 2 and 3, a sliding surface between the inner rotor 50 and the outer rotor 52 in the concave portion 42 b formed in the wall portion 42 a of the second case member 42 is, for example, a wall portion 42 a of the second case member 42. And a second pressure-feeding-side connection port 42d connected to the second oil supply oil passage 42c formed at the bottom.

  In the oil pump 22 configured as described above, when the second rotation shaft 26e provided in the gear mechanism 26 is driven to rotate during forward running of the vehicle, the oil pump 22 is connected to the second rotation shaft 26e as shown in FIG. The inner rotor 50 is driven to rotate around the third rotation axis C3 in the direction indicated by the arrow a via the pump drive shaft 48, and the outer rotor 52 is rotated about the fourth rotation axis C4 in the direction indicated by the arrow b. As a result, oil is sucked into the pump chamber S3 from the suction side connection port 46a formed in the pump cover 46, and the sucked oil flows inside the pump chamber S3 to the inner peripheral teeth 52a of the outer rotor 52 and the outer periphery of the inner rotor 50. It is taken into any one of a plurality of spaces formed by being partitioned by the teeth 50a. The oil taken into the space is compressed by being transferred to a circumferential position where the volume of the space decreases with the rotation of the inner rotor 50, and the oil whose pressure is increased by the compression is transferred to the pump cover 46. The liquid is discharged from the formed first pressure-feeding connection port 46b and the second pressure-feeding-side connection port 42d formed in the wall 42a of the second case member 42.

  As shown in FIG. 3, the pump drive shaft 48 has an insertion portion 48b inserted through an insertion hole 42e formed in the wall portion 42a of the second case member 42, and the pump drive shaft 48 has a more axial position than the insertion portion 48b. Is provided on the inner rotor 50 side in the third rotation axis C3 direction with respect to one end side of the direction, that is, the insertion portion 48b, and is concentric with the inner rotor 50 so as to be able to transmit power and to move relative to the inner rotor 50 in the third rotation axis C3 direction. The fitted first fitting portion 48c, a step portion 48d formed between the first fitting portion 48c and the insertion portion 48b in the pump drive shaft 48, and an axial direction of the pump drive shaft 48 more than the insertion portion 48b. Is provided on the other end side, that is, on the side opposite to the inner rotor 50 side in the direction of the third rotation axis C3 with respect to the insertion portion 48b, and is capable of transmitting power to the second rotation shaft 26e and the second rotation shaft 2 e, a second fitting portion 48e concentrically fitted in the third rotational axis C3 so as to be relatively movable in the direction of the third rotation axis C3, and a second portion 48e provided between the second fitting portion 48e and the insertion portion 48b on the pump drive shaft 48; A flange portion 48f having a larger outer diameter (diameter) D than the second fitting portion 48e and the insertion portion 48b is integrally formed.

  As shown in FIGS. 3 and 4, a pair of notches E1 and E2, each of which is formed by cutting out a part of an outer peripheral portion of the first fitting portion 48c, is formed in the first fitting portion 48c formed on the pump drive shaft 48. Is formed in the pump drive shaft 48 by fitting the first fitting portion 48c having the pair of cutouts E1 and E2 into the fitting hole 50b formed in the inner rotor 50. The first fitting portion 48c is fitted concentrically so as to be capable of transmitting power to the inner rotor 50, that is, unable to rotate relative to the inner rotor 50 and relatively movable with respect to the inner rotor 50 in the direction of the third rotation axis C3. Note that a pair of cutouts E1 and E2 are formed in the first fitting portion 48c, so that a step portion 48d is formed between the first fitting portion 48c and the insertion portion 48b.

  As shown in FIG. 3, an annular protrusion 26g protruding in a direction approaching the third rotation axis C3 is formed at an end 26f of the cylindrical second rotation shaft 26e on the pump drive shaft 48 side. In addition, an inner peripheral spline tooth 26h is formed on an inner peripheral surface of the projection 26g. The inner diameter D2 of the protrusion 26g is larger than the outer diameter of the second fitting portion 48e and smaller than the outer diameter D1 of the flange portion 48f. The outer diameter D3 of the insertion portion 48b of the pump drive shaft 48 is smaller than the outer diameter D1 of the flange 48f. On the outer peripheral surface of the second fitting portion 48e formed on the pump drive shaft 48, outer peripheral spline teeth 48g that spline fit with inner peripheral spline teeth 26h formed on the protrusion 26g of the second rotary shaft 26e are provided. Is formed. That is, the second fitting portion 48e formed on the pump drive shaft 48 is configured such that the outer circumferential spline teeth 48g formed on the second fitting portion 48e are formed on the inner circumferential spline teeth formed on the protrusion 26g of the second rotary shaft 26e. By being spline-fitted to 26h, power can be transmitted to the second rotation shaft 26e, that is, it cannot rotate relative to the second rotation shaft 26e and can move relative to the second rotation shaft 26e in the direction of the third rotation axis C3. To fit concentrically.

  As shown in FIG. 3, the insertion hole 42e formed in the wall portion 42a of the second case member 42 communicates the pump chamber S3 with the internal space S4 of the end 26f of the second rotating shaft 26e and performs the third rotation. It is a cylindrical hole extending in the direction of the axis C3. As shown in FIG. 3, the wall portion 42 a of the second case member 42 has an inner rotor side opening 42 g that is opened on the bottom surface 42 f of a concave portion 42 b formed in the wall portion 42 a, and the wall of the second case member 42. And a cylindrical protrusion 42h protruding in a cylindrical shape from the portion 42a in a direction approaching the flange portion 48f of the pump drive shaft 48. The internal space of the cylindrical protrusion 42h is a part of the insertion hole 42e.

  As shown in FIG. 3, the insertion portion 48 b of the pump drive shaft 48 is formed in a cylindrical shape, and the insertion portion 48 b of the pump drive shaft 48 is formed in a cylindrical shape formed on the wall 42 a of the second case member 42. The inner peripheral surface 42i of the insertion hole 42e having a shape is supported so as to be rotatable around the axis of the pump drive shaft 48, that is, the third rotation axis C3, and to be movable in the third rotation axis C3 direction. As shown in FIG. 3, in the axial direction of the pump drive shaft 48, that is, in the direction of the third rotation axis C <b> 3, between the step portion 48 d of the pump drive shaft 48 and the side surface 50 c of the inner rotor 50 on the second rotation shaft 26 e side. The gap B1 is larger than the gap B2 between the side surface 48h of the flange portion 48f of the pump drive shaft 48 on the inner rotor 50 side and the distal end surface 42j of the cylindrical protrusion 42h formed on the wall 42a of the second case member 42 ( B1> B2).

  In the pump drive shaft 48 configured as described above, the pump drive shaft 48 is directed toward the inner rotor 50 in the direction of the third rotation axis C3 with respect to the housing case 20, that is, the wall 42a of the second case member 42; Is relatively moved in the direction of arrow G shown in FIG. 4B, before the step portion 48d comes into contact with the side surface 50c of the inner rotor 50, the side surface 48h of the flange portion 48f is formed on the wall portion 42a of the second case member 42. The relative movement of the pump drive shaft 48 is restricted by contacting the tip end surface 42j of the portion 42h.

  As shown in FIG. 5, a pair of a first spiral groove (spiral groove) 48i and a second spiral groove (spiral groove) 48j are formed in the insertion portion 48b of the pump drive shaft 48. As shown in FIG. 5, the first spiral groove 48i and the second spiral groove 48j are formed in a circle in the direction of the third rotation axis C3 toward the inner rotor 50, that is, in the direction from the flange portion 48f to the first fitting portion 48c. It is formed so as to wind rightward around the outer peripheral surface of the columnar insertion portion 48b. The arrow F direction shown in FIG. 5 indicates that the second rotation shaft 26e, that is, the pump drive shaft 48 is counterclockwise with respect to the third rotation axis C3 when the vehicle is traveling forward when viewed from the direction from the flange portion 48f toward the inner rotor 50 side. Direction. That is, the torsional directions of the first spiral groove 48i and the second spiral groove 48j and the rotational direction of the pump drive shaft 48 at the time of forward movement are opposite directions when viewed from the direction from the flange 48f toward the inner rotor 50 side. When the pump drive shaft 48 rotates in the direction of arrow F to drive the oil pump 22, oil is discharged from the oil pump 22 to the second oil supply oil passage 42c, and is discharged to the second oil supply oil passage 42c. As shown in FIGS. 2 and 3, a part of the oil passes through the first oil passage 42 k and is supplied to, for example, the first bearing 34, or between the insertion portion 48 b of the pump drive shaft 48 and the second case member 42. It is supplied between the inner peripheral surface 42i of the insertion hole 42e formed in the wall 42a.

  In the pump drive shaft 48 configured as described above, when the pump drive shaft 48 rotates in the direction of arrow F during forward running of the vehicle, the pump drive shaft 48 is formed in the insertion portion 48b of the pump drive shaft 48 and the wall 42a of the second case member 42. The oil between the inner peripheral surface 42i of the inserted insertion hole 42e and the inner spiral surface 48i is directed toward the inner rotor 50 from the insertion hole 42e formed in the wall 42a of the second case member 42 by the first spiral groove 48i and the second spiral groove 48j. Pushed out. As a result, the pump drive shaft 48 causes the reaction force FS of the force for pushing out the oil by the first spiral groove 48i and the second spiral groove 48j, that is, the thrust force FS in the direction of the third rotation axis C3 to cause the wall of the second case member 42 to move. Relative to the inner rotor 50 in the direction of the third rotation axis C3 with respect to the inner rotor 50, ie, the second rotation shaft 26e in the direction of the third rotation axis C3 with respect to the wall 42a of the second case member 42. Move relatively toward. In other words, the first spiral groove 48i and the second spiral groove 48j formed in the insertion portion 48b allow the pump drive shaft 48 to rotate with the wall of the second case member 42 when the pump drive shaft 48 is rotating in the direction of arrow F. The thrust force FS is generated on the portion 42a in a direction opposite to the inner rotor 50 side in the third rotation axis C3 direction. When the thrust force FS causes the pump drive shaft 48 to move relatively to the wall portion 42a of the second case member 42 toward the second rotation shaft 26e in the direction of the third rotation axis C3, the flange portion 48f moves to the second position. The second case member 42 separates from the cylindrical protrusion 42h formed on the wall 42a of the case member 42 and comes into contact with a protrusion 26g formed on the second rotating shaft 26e.

  As described above, according to the drive device 16 of the present embodiment, the pump drive shaft 48 is inserted into the insertion portion 48b of the pump drive shaft 48 at the time of rotation of the pump drive shaft 48 during forward running of the vehicle. A first spiral groove 48i and a second spiral groove 48j for generating a thrust force FS toward the side opposite to the inner rotor 50 side in the direction of the third rotation axis C3 with respect to the case member 42 are formed. Therefore, when the pump drive shaft 48 rotates, that is, when the oil pump 22 is driven, the pump drive shaft 48 is housed by the thrust force FS generated by the first spiral groove 48i and the second spiral groove 48j formed in the insertion portion 48b. The second case member 42 of the case 20 is relatively moved in the direction of the third rotation axis C3 toward the side opposite to the inner rotor 50 side, and the flange 48 f of the pump drive shaft 48 is moved to the second case of the housing case 20. Since it becomes difficult to contact the cylindrical protrusion 42h formed on the member 42, loss of the driving force transmitted from the electric motor 12 to the driving wheels 14L and 14R when the oil pump 22 is driven can be suitably suppressed.

  Although the embodiments of the present invention have been described in detail with reference to the drawings, the present invention is applicable to other aspects.

  For example, in the driving device 16 of the above-described embodiment, the driving device 16 drives the pair of left and right driving wheels 14L and 14R by the electric motor 12 as the driving force source. For example, the pair of left and right drive wheels 14L, 14R may be driven by an engine or the like.

  In the drive device 16 of the above-described embodiment, the oil pump 22 is an internal gear oil pump, but may be an external gear oil pump, a vane oil pump, or the like. Any type of oil pump may be used as long as the oil pump discharges oil from the oil pump by rotating the rotor.

  Further, in the driving device 16 of the above-described embodiment, a pair of the first spiral groove 48i and the second spiral groove 48j are formed in the insertion portion 48b of the pump drive shaft 48, but the pair of first and second spiral grooves 48j are formed in the insertion portion 48b. Only one of the first spiral groove 48i and the second spiral groove 48j may be formed, or three or more spiral grooves may be formed in the insertion portion 48b.

  The above description is merely an embodiment, and the present invention can be embodied with various modifications and improvements based on the knowledge of those skilled in the art.

12: Electric motor (drive power source)
14L, 14R: drive wheel (wheel)
16: Drive unit (vehicle drive unit)
18: Power transmission mechanism 20: Housing case (case)
22: oil pump 26e: second rotating shaft (rotating shaft)
42e: insertion hole 46: pump cover 48: pump drive shaft 48b: insertion portion 48c: first fitting portion 48d: step portion 48e: second fitting portion 48f: flange portion 48i: first spiral groove (spiral groove).
48j: 2nd spiral groove (spiral groove)
50: Inner rotor (pump rotor)
FS: Thrust force S3: Pump room

Claims (1)

A power transmission mechanism that transmits driving force from a driving force source to wheels, a case that houses the power transmission mechanism, a rotation shaft that is provided in the power transmission mechanism and that is rotatably supported by the case, And a pump cover housed in a pump chamber formed by a pump cover attached to the case. The pump rotor is driven to rotate by a pump drive shaft connected to the rotation shaft to discharge oil. An oil pump, and a vehicle drive device comprising:
The pump drive shaft,
An insertion portion inserted into an insertion hole formed in the case,
A first fitting portion that is provided on one end side in the axial direction with respect to the insertion portion and that is fitted concentrically so as to be capable of transmitting power to the pump rotor and relatively moving in the axial direction with respect to the pump rotor;
A step portion formed between the first fitting portion and the insertion portion;
A second fitting portion that is provided on the other end side in the axial direction with respect to the insertion portion and is fitted concentrically so as to be capable of transmitting power to the rotating shaft and relatively moving in the axial direction with respect to the rotating shaft; ,
The step portion is provided between the second fitting portion and the insertion portion, and when the pump drive shaft is relatively moved toward the one end portion side in the axial direction with respect to the case, the step portion is formed by the pump rotor. Abutting against the case before abutting against the case to regulate the relative movement of the pump drive shaft, a flange portion having a larger diameter than the insertion portion;
With
The insertion portion has a spiral groove that generates a thrust force toward the other end of the pump drive shaft with respect to the case when the pump drive shaft rotates. Vehicle drive device.

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