WO2019156196A1 - Structure d'alimentation en lubrifiant et dispositif d'entraînement de moteur-roue - Google Patents

Structure d'alimentation en lubrifiant et dispositif d'entraînement de moteur-roue Download PDF

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Publication number
WO2019156196A1
WO2019156196A1 PCT/JP2019/004538 JP2019004538W WO2019156196A1 WO 2019156196 A1 WO2019156196 A1 WO 2019156196A1 JP 2019004538 W JP2019004538 W JP 2019004538W WO 2019156196 A1 WO2019156196 A1 WO 2019156196A1
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WO
WIPO (PCT)
Prior art keywords
oil
lubricating oil
receiving chamber
supply structure
casing
Prior art date
Application number
PCT/JP2019/004538
Other languages
English (en)
Japanese (ja)
Inventor
華夏 李
鈴木　稔
四郎 田村
佐藤　勝則
早織 杉浦
Original Assignee
Ntn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
Priority claimed from JP2019020232A external-priority patent/JP2019140906A/ja
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Priority to CN201980012074.8A priority Critical patent/CN111699618A/zh
Publication of WO2019156196A1 publication Critical patent/WO2019156196A1/fr

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    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K9/00—Arrangements for cooling or ventilating
    • H02K9/19—Arrangements for cooling or ventilating for machines with closed casing and closed-circuit cooling using a liquid cooling medium, e.g. oil
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K7/00—Disposition of motor in, or adjacent to, traction wheel
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/64—Electric machine technologies in electromobility

Definitions

  • the present invention relates to a lubricating oil supply structure in an in-wheel motor drive device, and more particularly to a lubricating oil supply structure including an oil pump.
  • An in-wheel motor provided with a motor part having a motor rotation shaft for driving a wheel, a wheel hub bearing part, and a reduction part for reducing the rotation of the motor rotation shaft and transmitting it to the wheel hub bearing part.
  • lubricating oil is used for cooling the heat generating element (stator) in the motor section and for lubricating the rotating elements (gears and bearings) constituting the speed reducing mechanism in the speed reducing section. .
  • Patent Document 1 an oil pump is provided at one end of a rotating shaft that is rotated by the output torque of a motor, and lubricating oil pumped by the oil pump passes through the oil passage to the motor.
  • An in-wheel motor drive device configured to be supplied to the outer periphery of the stator core and reach the coil end is disclosed.
  • Patent Document 2 discloses that an oil supply device of an in-wheel motor drive device includes an outer periphery of a stator core and a coil of a motor from an oil supply path connected to a discharge port of an oil pump. It is disclosed that lubricating oil is guided to a motor bearing.
  • JP 2005-73364 A Patent No. 3968333
  • the motor unit is driven by the current flowing through the stator coil, while copper loss caused by coil resistance also causes the motor unit to generate heat.
  • copper loss due to a large current becomes the main cause of heat generation, and therefore it is required to cool the coil when cooling the motor unit.
  • the lubricating oil supply structure disclosed in Patent Document 1 is configured so that the lubricating oil supplied from the oil passage to the outer periphery of the stator core reaches the coil end via the outer periphery of the stator core, so that the coil is cooled. It becomes possible to do.
  • the rotation speed of the oil pump is proportional to the rotation speed of the motor rotation shaft. Therefore, the discharge flow rate from the oil pump is also proportional to the rotation speed of the motor rotation shaft.
  • the oil pump can also discharge the lubricating oil only with a small flow rate, so that a small amount of lubricating oil is supplied to the outer periphery of the stator core from the opening through the oil passage.
  • a small amount of lubricating oil flows preferentially by gravity in the outer circumferential direction of the stator core, and since it reaches the coil end at the axial end of the stator after that, the cooling of the coil becomes insufficient. There is concern.
  • Patent Document 2 discloses a configuration in which lubricating oil is directly supplied to the coil end of the stator, but from the downward opening provided in the oil supply passage extending in the axial direction above the stator in the radial direction. The lubricating oil is allowed to flow out. In this case, since the lubricating oil is discharged in the form of a beam from the opening provided in the oil supply path, the lubricating oil rebounds and the coil cannot be cooled effectively.
  • the present invention has been made to solve the above-described problems, and an object thereof is to provide a lubricating oil supply structure capable of efficiently cooling a motor unit.
  • a lubrication oil supply structure is a lubrication oil supply structure in an in-wheel motor drive device including a motor unit including a stator.
  • the lubrication oil supply structure accommodates the motor unit and surrounds the outline of the in-wheel motor drive device.
  • a casing to be formed, an oil tank provided in a lower part of the casing and storing lubricating oil, and an oil pump for pumping the lubricating oil from the oil tank are provided.
  • this lubricating oil supply structure is arranged along the axial direction of the motor unit at a position above the stator, and has an oil passage having at least one oil hole for discharging the lubricating oil pumped up by the oil pump in the radial direction.
  • a lubricating oil guide for guiding the lubricating oil discharged from the oil hole to the coil end of the stator.
  • the lubricant guide portion includes an oil receiving chamber that receives the lubricant discharged from the oil hole.
  • the oil receiving chamber is disposed so as to face the oil hole and surround the outer periphery of the oil passage, and the cross-sectional area of the oil receiving chamber is larger than the passage area of the oil passage.
  • the oil hole includes a first hole and a second hole that are disposed within the axial width of the core portion of the stator and have different axial positions.
  • the oil receiving chamber is preferably partitioned into a first oil receiving chamber that receives the lubricating oil discharged from the first hole and a second oil receiving chamber that receives the lubricating oil discharged from the second hole.
  • At least one of the first oil receiving chamber and the second oil receiving chamber is inclined along the axial direction so that the lower end height becomes lower as the distance from the convex portion decreases.
  • the oil receiving chamber is formed in a part of the casing.
  • the lubricating oil guide portion further includes an oil pouring path that communicates with the oil receiving chamber and extends in the axial direction, and has a spout for lubricating oil formed at the tip of the coil end.
  • the lubricating oil guide portion further includes a splash preventing member that is disposed facing the pouring spout of the oil pouring passage in the axial direction and prevents the lubricating oil flowing out from the pouring spout.
  • the oil passage is constituted by one or a plurality of tubular members attached and fixed to the casing.
  • the scattering prevention member may include a plate member formed integrally with the tubular member.
  • the casing may have a wall portion facing the oil pouring path in the axial direction
  • the scattering prevention member may include a convex portion formed on the wall portion of the casing.
  • the lubricating oil guide further includes a distribution member for distributing the lubricating oil flowing out from the spout of the oil pouring path to a plurality of coil ends.
  • the lubricant guide portion may further include a distribution member for distributing the lubricant oil to the plurality of coil ends, and a scattering prevention member that is provided integrally with the distribution member and prevents the lubricant from scattering. Good.
  • the oil passage is constituted by a tubular member in which a large-diameter fitting portion is formed at one end.
  • the casing includes a wall portion having a connection portion that faces the scattering prevention member provided integrally with the distribution member in the axial direction and receives the fitting portion of the tubular member.
  • the distance between the scattering prevention member and the connection portion is equal to or larger than the axial dimension of the fitting portion of the tubular member.
  • the in-wheel motor drive device further includes a speed reducing portion that decelerates rotation of the motor rotation shaft of the motor portion, and the casing has a partition portion that partitions the motor portion and the speed reducing portion in the axial direction.
  • the oil passage is constituted by one tubular member that penetrates the partition wall.
  • the lubricating oil discharged in the radial direction from the oil hole is guided to the coil end of the stator by the lubricating oil guide portion, so that the motor portion can be efficiently cooled.
  • FIG. 5 is a longitudinal sectional view showing an in-wheel motor drive device according to Embodiments 1 to 4 of the present invention cut along a predetermined plane and developed.
  • FIG. 5 is a cross-sectional view showing the internal structure of the speed reduction portion of the in-wheel motor drive device according to Embodiments 1 to 4 of the present invention.
  • It is sectional drawing which shows typically the principal part of the supply structure of the lubricating oil which concerns on Embodiment 1 of this invention. It is a figure which shows typically the oil channel
  • Embodiment 1 of this invention it is sectional drawing which shows typically the other structural example of an oil path. It is a figure which shows typically the oil channel
  • Embodiment 2 of this invention it is a front view of the guidance member which integrally contains a distribution member and a scattering prevention member. It is a top view of the guidance member in Embodiment 2 of the present invention. It is a perspective view of the guidance member in Embodiment 2 of the present invention. It is sectional drawing which shows the attachment state of the guide member in Embodiment 2 of this invention. In Embodiment 2 of this invention, it is sectional drawing which shows typically the other structural example of an oil path.
  • Embodiment 5 of this invention It is a figure which shows typically the internal structure of the deceleration part of the in-wheel motor drive device which concerns on Embodiment 5 of this invention. It is sectional drawing which shows typically the principal part of the supply structure of the lubricating oil which concerns on Embodiment 5 of this invention. In Embodiment 5 of this invention, it is a figure which shows typically the example of an internal structure by the side of the deceleration chamber of a casing. In Embodiment 5 of this invention, it is the perspective view which looked at the longitudinal cross-section of the upper part of the motor casing in which the oil pipe was penetrated from the deceleration chamber side. It is a figure which shows typically the lubricating oil guide part in Embodiment 5 of this invention.
  • Embodiment 5 of this invention it is the figure which looked at the motor chamber from the inboard side in the state which removed the motor casing cover.
  • Embodiment 5 of this invention it is a figure which shows typically the internal structural example by the side of the motor chamber of a casing.
  • It is a perspective view which shows typically the structural example of the motor casing cover in Embodiment 5 of this invention.
  • It is a longitudinal cross-sectional view which shows typically the sensor chamber provided in the motor casing cover in Embodiment 5 of this invention.
  • Example of basic configuration of in-wheel drive device a basic configuration example of an in-wheel motor drive device 1 that employs a lubricating oil supply structure according to an embodiment of the present invention will be described with reference to FIGS. 1 and 2.
  • the in-wheel motor drive device 1 is mounted on a passenger car such as an electric vehicle and a hybrid vehicle.
  • FIG. 1 is a longitudinal sectional view showing an in-wheel motor drive device 1 according to an embodiment of the present invention cut along a predetermined plane and developed.
  • FIG. 2 is a cross-sectional view showing the internal structure of the speed reduction unit 31 of the in-wheel motor drive device 1, and schematically shows a state viewed from the outside in the vehicle width direction.
  • the predetermined plane shown in FIG. 1 is a developed plane obtained by connecting the plane including the axis M and the axis N shown in FIG. 2 and the plane including the axis N and the axis O in this order.
  • the left side of the drawing represents the vehicle width direction outside (outboard side)
  • the right side of the drawing represents the vehicle width direction inside (inboard side).
  • each gear inside the speed reduction unit 31 is represented by a tip circle, and individual teeth are omitted.
  • the in-wheel motor drive device 1 includes a wheel hub bearing unit 11 provided at the center of the wheel W, a motor unit 21 that drives the wheel, and a deceleration that decelerates the rotation of the motor unit 21 and transmits it to the wheel hub bearing unit 11. Part 31.
  • the motor part 21 and the speed reduction part 31 are arranged offset from the axis O of the wheel hub bearing part 11.
  • the axis O extends in the vehicle width direction and coincides with the axle. In the present embodiment, it is assumed that one side in the axis O direction is the outboard side and the other side in the axis O direction is the inboard side.
  • the in-wheel motor drive device 1 is a vehicle motor drive device that drives wheels of an electric vehicle.
  • the in-wheel motor drive device 1 is connected to a vehicle body (not shown).
  • the in-wheel motor drive device 1 can drive an electric vehicle at a speed of 0 to 180 km / h.
  • the wheel hub bearing portion 11 is a rotating inner ring / fixed outer ring, and includes an inner ring 12 as a rotating wheel (hub wheel) coupled to the wheel wheel W, and an outer ring as a fixed ring disposed coaxially on the outer diameter side of the inner ring 12. 13 and a plurality of rolling elements 14 arranged in an annular space between the inner ring 12 and the outer ring 13.
  • the center of rotation of the inner ring 12 coincides with an axis O passing through the center of the wheel hub bearing portion 11.
  • the outer ring 13 penetrates the front portion 39f of the main body casing 39 and is connected and fixed to the front portion 39f.
  • the front portion 39 f is a casing wall portion that covers one end of the speed reduction portion 31 in the axis O direction of the main body casing 39.
  • a plurality of outer ring protrusions protruding in the outer diameter direction are provided on the outer peripheral surface of the outer ring 13 at different positions in the circumferential direction, and one side of the axis O direction with respect to the through hole provided in each outer ring protrusion
  • the bolt is passed through.
  • the shaft portion of each bolt is screwed into a female screw hole formed in the front portion 39 f of the main body casing 39.
  • the carrier member 61 is connected and fixed to the outer ring 13.
  • the carrier member 61 is located on the other side of the outer ring protruding portion 13g in the axis O direction, and a bolt 62 is passed from one side of the axis O direction to the through hole of the outer ring protruding portion 13g and the female screw hole of the carrier member 61.
  • the carrier member 61 is fixed to the main body casing 39 by a bolt 63 passed from the other side in the axis O direction.
  • the inner ring 12 is a cylindrical body longer than the outer ring 13 and is passed through the center hole of the outer ring 13.
  • a coupling portion 12f is formed at one end of the inner ring 12 protruding from the outer ring 13 to the outside (outboard side) in the axis O direction.
  • the coupling portion 12f is a flange and constitutes a coupling portion for coupling coaxially with the brake rotor BD and the wheel.
  • the inner ring 12 is coupled to the wheel W at the coupling portion 12f and rotates integrally with the wheel.
  • a plurality of rows of rolling elements 14 are arranged.
  • the outer peripheral surface of the central portion of the inner ring 12 in the direction of the axis O constitutes the inner raceway surface of the plurality of rolling elements 14 arranged in the first row.
  • An inner race 12r is fitted to the outer periphery of the other end of the inner ring 12 in the axis O direction.
  • the outer peripheral surface of the inner race 12r constitutes the inner race of the plurality of rolling elements 14 arranged in the second row.
  • the inner peripheral surface at one end of the outer ring 13 in the direction of the axis O constitutes the outer raceway surface of the rolling elements 14 in the first row.
  • An inner peripheral surface of the other end portion of the outer ring 13 in the axis O direction forms an outer raceway surface of the rolling elements 14 in the second row.
  • a sealing material 16 is further interposed in the annular space between the inner ring 12 and the outer ring 13. The sealing material 16 seals both ends of the annular space to prevent intrusion of dust and foreign matter.
  • the output shaft 38 of the speed reduction part 31 is inserted into the center hole at the other end in the axis O direction of the inner ring 12 and is spline-fitted.
  • the motor unit 21 has a motor rotating shaft 22, a rotor 23, and a stator 24, and is sequentially arranged from the axis M of the motor unit 21 to the outer diameter side in this order.
  • the motor unit 21 is an inner rotor / outer stator type radial gap motor, but may be of other types.
  • the motor unit 21 may be an axial gap motor.
  • the motor unit 21 is accommodated in a motor casing 29.
  • the motor casing 29 surrounds the outer periphery of the stator 24.
  • One end of the motor casing 29 in the direction of the axis M is coupled to the back surface portion 39 b of the main body casing 39.
  • the other end of the motor casing 29 in the axis M direction is sealed with a plate-like motor casing cover 29v.
  • the back surface portion 39 b is a casing wall portion that covers the other end of the main body casing 39 in the direction of the axis M (axis O direction) of the speed reduction portion 31.
  • the main body casing 39, the motor casing 29, and the motor casing cover (rear cover) 29 v constitute the casing 10 that forms the outline of the in-wheel motor driving device 1.
  • the stator 24 includes a cylindrical core portion (hereinafter referred to as “stator core”) 25 and a coil 26 wound around the stator core 25.
  • the stator core 25 is formed by laminating ring-shaped steel plates in the axis M direction.
  • Both end portions of the motor rotating shaft 22 are rotatably supported by the back portion 39b of the main body casing 39 and the motor casing cover 29v via rolling bearings 27 and 28.
  • An axis M serving as the rotation center of the motor rotation shaft 22 and the rotor 23 extends in parallel with the axis O of the wheel hub bearing portion 11. That is, the motor unit 21 is disposed offset from the axis O of the wheel hub bearing unit 11.
  • the axis M of the motor unit 21 is offset from the axis O in the vehicle front-rear direction, and specifically, is disposed in front of the vehicle relative to the axis O.
  • the speed reduction unit 31 includes an input shaft 32 that is coaxially coupled to the motor rotation shaft 22 of the motor unit 21, an input gear 33 that is provided coaxially on the outer peripheral surface of the input shaft 32, a plurality of intermediate gears 34 and 36, An intermediate shaft 35 coupled to the center of the gears 34, 36, an output shaft 38 coupled coaxially to the inner ring 12 of the wheel hub bearing portion 11, and an output gear 37 provided coaxially on the outer peripheral surface of the output shaft 38.
  • the plurality of gears and the rotation shaft of the speed reduction unit 31 are accommodated in the main body casing 39.
  • the main body casing 39 is also referred to as a speed reduction part casing because it forms an outline of the speed reduction part 31.
  • the input gear 33 is a helical gear with external teeth.
  • the input shaft 32 has a hollow structure, and one end in the axial direction of the motor rotation shaft 22 is inserted into the hollow portion 32 h of the input shaft 32. Thereby, the motor rotating shaft 22 is spline-fitted (or serrated fitted) to the input shaft 32 so as not to be relatively rotatable.
  • the input shaft 32 is rotatably supported by the front portion 39f and the back portion 39b of the main body casing 39 via rolling bearings 32a and 32b on both ends of the input gear 33.
  • the axis N that is the center of rotation of the intermediate shaft 35 of the speed reduction part 31 extends parallel to the axis O. Both ends of the intermediate shaft 35 are rotatably supported by the front portion 39f and the back portion 39b of the main body casing 39 via bearings 35a and 35b.
  • a first intermediate gear 34 and a second intermediate gear 36 are provided coaxially with the axis N of the intermediate shaft 35 at the center of the intermediate shaft 35.
  • the first intermediate gear 34 and the second intermediate gear 36 are external helical gears, and the diameter of the first intermediate gear 34 is larger than the diameter of the second intermediate gear 36.
  • the large-diameter first intermediate gear 34 is disposed on the other side in the axis N direction with respect to the second intermediate gear 36, and meshes with the small-diameter input gear 33.
  • the small-diameter second intermediate gear 36 is disposed on one side in the axis N direction relative to the first intermediate gear 34 and meshes with the large-diameter output gear 37.
  • the output gear 37 is a helical gear with external teeth, and is provided coaxially at the center of the output shaft 38.
  • the output shaft 38 extends along the axis O.
  • One end of the output shaft 38 in the direction of the axis O is inserted into the center hole of the inner ring 12 and is fitted so as not to be relatively rotatable.
  • Such fitting is spline fitting or serration fitting.
  • a central portion (one end side) of the output shaft 38 in the axis O direction is rotatably supported by the front portion 39f of the main body casing 39 via the rolling bearing 38a.
  • the other end portion (the other end side) in the axis O direction of the output shaft 38 is rotatably supported by the back surface portion 39b of the main body casing 39 via the rolling bearing 38b.
  • the reduction gear 31 is configured to engage the input shaft 32 by meshing the small-diameter drive gear and the large-diameter driven gear, that is, meshing the input gear 33 and the first intermediate gear 34, and meshing the second intermediate gear 36 and the output gear 37.
  • the rotation is decelerated and transmitted to the output shaft 38.
  • the rotating elements from the input shaft 32 to the output shaft 38 of the speed reduction unit 31 constitute a drive transmission path for transmitting the rotation of the motor unit 21 to the inner ring 12.
  • the input shaft 32, the intermediate shaft 35, and the output shaft 38 are supported at both ends by the rolling bearing described above. These rolling bearings 32a, 35a, 38a, 32b, 35b, and 38b are radial bearings.
  • the main body casing 39 includes a cylindrical part, and a plate-like front part 39f and a rear part 39b covering both ends of the cylindrical part.
  • the cylindrical portion covers the internal parts of the speed reducing portion 31 so as to surround the axes O, N, and M extending in parallel with each other.
  • the plate-shaped front portion 39f covers the internal parts of the speed reduction portion 31 from one side in the axial direction.
  • the plate-like back surface portion 39b covers the internal parts of the speed reducing portion 31 from the other side in the axial direction.
  • the back surface portion 39 b of the main body casing 39 is a partition wall that is coupled to the motor casing 29 and partitions the internal space of the speed reduction portion 31 and the internal space of the motor portion 21.
  • the motor casing 29 is supported by the main body casing 39 and protrudes from the main body casing 39 to the other side in the axial direction.
  • the rotor 23 of the motor unit 21 rotates and outputs rotation from the motor rotation shaft 22 to the speed reduction unit 31.
  • the deceleration unit 31 decelerates the rotation input from the motor unit 21 to the input shaft 32 and outputs the rotation from the output shaft 38 to the wheel hub bearing unit 11.
  • the inner ring 12 of the wheel hub bearing portion 11 rotates at the same rotational speed as the output shaft 38 and drives a wheel (not shown) attached and fixed to the inner ring 12.
  • an oil tank 40 is provided at the lower part of the main body casing 39.
  • the oil tank 40 is disposed at a lower position than the motor unit 21. Lubricating oil is stored in the oil tank 40 occupying the lower part of the internal space of the main casing 39.
  • Lubricating oil is used to lubricate the rotating elements of the motor unit 21 and the speed reducing unit 31 and to cool the stator 24 that is a heat generating element of the motor unit 21.
  • the lubricating oil supply structure in the in-wheel motor drive device 1 will be described in detail.
  • the reduction part 31 of the in-wheel motor drive device 1 showed the example which is a 3 axis
  • a reduction part has other kinds of gear reductions, such as a 4 axis
  • a speed reducer without a gear may be used.
  • the lubricating oil supply structure in the in-wheel motor drive device 1 includes a casing 10 that encloses lubricating oil, an oil tank 40 that is provided in a lower portion of the casing 10 and stores lubricating oil, and an oil An oil pump 43 for pumping lubricating oil from the tank 40 and an oil passage 50 arranged along the axis M direction at a position above the stator 24 are provided as preconditions.
  • a direction along the axis M direction of the motor unit 21 is simply referred to as an axial direction.
  • the oil pump 43 sucks lubricating oil from the oil tank 40 through the suction oil passage 41 and discharges the sucked lubricating oil to the discharge oil passage 45.
  • the oil pump 43 is driven in conjunction with the rotation of the motor rotating shaft 22.
  • the oil pump 43 is coupled to the output shaft 38 coaxially and is driven by the output shaft 38, for example. In this case, the oil pump 43 is driven at the same rotational speed as the wheels.
  • the oil pump 43 is, for example, a trochoid pump having an outer rotor and an inner rotor.
  • the other end portion 38f in the axis O direction of the output shaft 38 extends through the back surface portion 39b of the main body casing 39, and the oil pump 43 is connected to the output shaft 38 protruding from the back surface portion 39b. It couple
  • the suction oil passage 41 is led from the oil tank 40 to the pump chamber 46 through the back surface portion 39b of the main body casing 39 (that is, the partition wall portion between the main body casing 39 and the motor casing 29).
  • the pump chamber 46 is provided, for example, in an extended portion of the motor casing 29 that extends to the vehicle rear side from the position of the outer peripheral surface of the motor unit 21 (stator 24).
  • the oil tank 40 may be provided in the lower part of the motor casing 29.
  • the discharge oil passage 45 includes a rising oil passage 45a formed in the wall thickness of the motor casing cover 29v.
  • the rising oil passage 45a extends in the vertical direction, and is connected to one end of the oil passage 50 at the upper end.
  • oil holes a plurality of holes (hereinafter referred to as "oil holes") 59 are provided at intervals from each other along the axial direction. That is, the oil passage 50 is provided with a plurality of holes 59 so as to be orthogonal to the axial direction. Thereby, the lubricating oil flowing through the oil passage 50 is discharged from the oil hole 59 in the radial direction.
  • the lubricating oil discharged from the oil hole 59 of the oil passage 50 is not supplied to the coil 26 of the stator 24 as it is, but is supplied to the coil 26 (coil end) via the lubricating oil guide portion 7.
  • the lubricating oil supply structure according to the present embodiment includes the lubricating oil guide portion 7 that guides the lubricating oil discharged from the oil hole 59 to the coil end of the stator 24.
  • FIG. 3 is a cross-sectional view schematically showing a main part of the lubricating oil supply structure according to the present embodiment.
  • 4 and 5 are diagrams schematically showing the oil passage 50 and the lubricating oil guide portion 7 in the present embodiment.
  • FIG. 4 shows the entire stator 24, and FIG. The parts are shown.
  • the oil passage 50 is composed of two (a plurality of) tubular members (hereinafter referred to as “oil pipes”) 51 and 52.
  • the oil pipes 51 and 52 are connected in series, and the oil pipe 51 is disposed on the upstream side of the oil pipe 52.
  • the oil pipes 51 and 52 are formed in a cylindrical shape, and the diameters (inner diameter and outer diameter) of the oil pipes 51 and 52 are equal to each other.
  • One end of the oil pipe 51 is connected to the upper end of the rising oil passage 45 a, and the other end of the oil pipe 51 is connected to one end of the oil pipe 52.
  • the other end of the oil pipe 52 is closed, but the oil pipe 52 includes an oil pipe (an oil pipe 57 indicated by an imaginary line in FIG. 2) disposed in the main body casing 39, and a main body casing. 39 may be connected at the back portion 39b. That is, an oil passage (an oil passage constituted by the oil pipe 57) disposed in the main body casing 39 may be provided on the downstream side of the oil passage 50 disposed in the motor casing 29. Alternatively, the oil pipe 52 may extend through the back surface portion 39b of the main body casing 39, and may be disposed across the motor chamber and the deceleration chamber.
  • the oil pipes 51 and 52 are attached and fixed to the upper part of the motor casing 29.
  • the upper end wall of the motor casing 29 is bulged inward in the radial direction, and the oil passage 50 is disposed so as to penetrate this bulged portion (hereinafter referred to as “thick portion”) 29t in the axial direction.
  • Thick portion shows a transverse section of the thick portion 29t of the motor casing 29
  • FIG. 5 shows a longitudinal section of the thick portion 29t of the motor casing 29.
  • FIG. 5 shows a state in which the oil passage 50 is looked up from below.
  • the thick portion 29t is disposed within the axial width of the stator core 25 (within the range from one axial end to the other end) with respect to the axial position.
  • the lower end of the thick portion 29t may be in contact with the outer peripheral surface of the stator core 25.
  • the thick part 29t has a through hole 29h extending in the axial direction.
  • Part of the oil pipe 51 passes through the opening on the other axial side (inboard side) of the through hole 29h, and part of the oil pipe 52 passes through the opening on one side (outboard side) in the axial direction of the through hole 29h.
  • the diameter of the through hole 29h is larger than the outer diameter of the oil pipes 51 and 52.
  • the oil pipe 51 has a flange portion 51a protruding upward, and this flange portion 51a is bolted to the other end surface in the axial direction of the thick portion 29t.
  • the flange portion 51a has a through hole facing a female screw hole provided on the other end surface in the axial direction of the thick portion 29t. From the other side in the axial direction, the through hole of the flange portion 51a and the female screw of the thick portion 29t are provided. Bolts 63 are passed through the holes.
  • the oil pipe 52 has a flange portion 52a protruding upward, and this flange portion 52a is bolted to one end surface in the axial direction of the thick portion 29t. Thereby, rotation of the oil pipes 51 and 52 is prevented.
  • One end of the oil pipe 51 is connected to the upper end of the rising oil passage 45a, and the other end of the oil pipe 51 is disposed in the thick portion 29t.
  • One end of the oil pipe 52 is disposed in the thick part 29t so as to be adjacent to the other end of the oil pipe 51, and the other end of the oil pipe 52 is disposed so as to protrude outward from the thick part 29t.
  • the axial direction position of the other end of the oil pipe 52 is a position on the outer side (one axial direction side) of the coil end 26e positioned on one axial direction side of the stator core 25.
  • fitting portions 53 and 54 having a diameter larger than that of the main body portion (center portion) are provided.
  • a fitting portion 55 having a larger diameter than the main body portion (center portion) is also provided at one end of the oil pipe 52.
  • the fitting portion 53 on one end side of the oil pipe 51 is fitted into an opening (upper end portion of the rising oil passage 45a) provided on the inner end face of the motor casing cover 29v.
  • the fitting part 54 on the other end side of the oil pipe 51 and the fitting part 55 on one end of the oil pipe 52 are fitted into the through hole 29 h of the thick part 29 t of the motor casing 29.
  • an O-ring 56 is provided on the outer peripheral surface of each fitting portion, and leakage of lubricating oil in each fitting portion is prevented.
  • the other end of the oil pipe 51 and one end of the oil pipe 52 may be arranged slightly apart.
  • At least one oil hole 59 is provided in the main body portion of each oil pipe 51, 52. That is, the oil passage 50 includes at least two oil holes (first hole, second hole) 59 having different axial positions. More specifically, at least one oil hole 59 is orthogonal to the oil passage 50 on both the one side and the other side in the axial direction with the axially central plane of the stator 24 (shown in phantom lines in FIG. 3) as a boundary. Is provided.
  • the oil holes 59 of the oil pipes 51 and 52 are provided in the axial width of the stator core 25. That is, the axial position of the oil hole 59 is between one end and the other end of the stator core 25 in the axial direction.
  • the oil hole 59 is provided in a lower region of each of the oil pipes 51 and 52 and flows out (discharges) a part of the lubricating oil flowing through the oil passage 50 downward.
  • the lubricating oil discharged from the oil hole 59 is guided to the coil end 26e through the lubricating oil guide portion 7.
  • the coil end 26e corresponds to a bent portion of the coil 26 formed on the outer sides of both axial end surfaces of the stator core 25. As shown in FIG. 4, a plurality of coil ends 26e are arranged radially on each of one side and the other side of the stator core 25 in the axial direction.
  • the lubricating oil guide portion 7 includes an oil receiving chamber 71 that receives the lubricating oil discharged from the oil hole 59 and an oil pouring path 72 that communicates with the oil receiving chamber 71 and extends along the axial direction. .
  • the oil receiving chamber 71 is disposed so as to face the oil hole 59 of the oil passage 50 and surround (a part of) the outer periphery of the oil passage 50.
  • the oil receiving chamber 71 is a space for temporarily storing lubricating oil discharged from the oil hole 59 in the radial direction.
  • the oil receiving chamber 71 extends along the axial direction and has, for example, a circular cross section (ring-shaped cross section).
  • the axis of the oil receiving chamber 71 coincides with the axis of the oil passage 50.
  • the oil receiving chamber 71 is formed such that its cross-sectional area is larger than the passage area of the oil passage 50.
  • the oil receiving chamber 71 is formed in a part of the motor casing 29, that is, in the thick portion 29t. That is, the oil receiving chamber 71 is formed by an annular space between the inner peripheral surface of the through hole 29h of the thick portion 29t and the outer peripheral surfaces of the oil pipes 51 and 52.
  • the thick portion 29t constitutes the outer peripheral portion of the oil receiving chamber 71.
  • the oil receiving chamber 71 is divided into two oil receiving chambers 71a and 71b in the axial direction.
  • the oil receiving chamber 71 a is formed on the other axial side (inboard side) of the fitting portion 54 of the oil pipe 51 and faces the oil hole 59 of the oil pipe 51.
  • the oil receiving chamber 71 b is formed on one axial side (outboard side) of the fitting portion 55 of the oil pipe 52 and faces the oil hole 59 of the oil pipe 52.
  • the lubricating oil discharged from the oil hole 59 of the oil pipe 51 is received in the oil receiving chamber 71a, and the fitting portion 54 of the oil pipe 51 prevents the flow to the other oil receiving chamber 71b. Since the cross-sectional shape of the oil receiving chamber 71a is circular, the lubricating oil flows in the circumferential direction (around the oil pipe 51) in the oil receiving chamber 71a. The lubricating oil received by the oil receiving chamber 71a flows out from the opening at the other end in the axial direction.
  • Lubricating oil discharged from the oil hole 59 of the oil pipe 52 is received in the oil receiving chamber 71b, and the fitting portion 55 of the oil pipe 52 prevents the flow to the other oil receiving chamber 71a. Since the cross-sectional shape of the oil receiving chamber 71b is also circular, the lubricating oil flows in the circumferential direction (around the oil pipe 52) also in the oil receiving chamber 71b. The lubricating oil received by the oil receiving chamber 71b flows out from the opening at one end in the axial direction.
  • the open end side of the oil receiving chambers 71a and 71b is referred to as the downstream side, and the fitting portions 54 and 55 side is referred to as the upstream side.
  • the axial position of the oil hole 59 is preferably an upstream position. That is, it is desirable that the two oil holes 59 are disposed closer to the axial center surface of the stator core 25.
  • the lubricating oil discharged from the oil hole 59 of the oil passage 50 is more than when it flows in the oil passage 50.
  • the oil flows out from the open ends of the oil receiving chambers 71a and 71b at a slow flow rate.
  • the oil receiving chamber 71 when it is not necessary to distinguish the two oil receiving chambers 71a and 71b, they are simply referred to as the oil receiving chamber 71.
  • the oil pouring path 72 communicates with the downstream end of the oil receiving chamber 71 and extends along the axial direction. Specifically, a pair of oil pouring paths 72 are provided so as to communicate with the open ends of the oil receiving chambers 71a and 71b. A spout 72a for pouring lubricating oil into the coil end 26e is formed at the tip of each oil pouring path 72.
  • the cross-sectional shape of the oil pouring path 72 is, for example, a semicircular shape.
  • the oil pouring path 72 is formed by an arc-shaped member 72m connected to the axial end of the thick portion 29t of the motor casing 29.
  • the arc-shaped member 72m may be a part of the thick portion 29t. That is, the oil pouring path 72 may also be formed in a part of the motor casing 29.
  • the semicircular radius of the oil pouring channel 72 is larger than the circular radius of the oil receiving chamber 71.
  • the semicircular center point of the oil pouring channel 72 coincides with the center (axial center) of the oil passage 50 and the oil receiving chamber 71.
  • a step in the vertical direction is formed between the inner peripheral surface of the oil receiving chamber 71 and the inner peripheral surface of the oil pouring path 72, so that the lubricating oil received by the oil receiving chamber 71 is at the open end (downstream).
  • the oil flows down from the side end portion to the oil pouring path 72. Therefore, the flow in the circumferential direction generated in the oil receiving chamber 71 in the oil pouring path 72 can be restricted, and the flow direction of the lubricating oil can be converged in the axial direction.
  • the axial position of the spout 72a of the oil pouring path 72 is near the boundary position between the stator core 25 and the coil end 26e. Therefore, the lubricating oil whose flow direction is converged in the axial direction in the oil pouring path 72 flows out from the pouring spout 72a as it is, and flows down to the coil end 26e below (typically, the coil end 26e located at the uppermost position). . That is, the lubricating oil flowing out from the spout 72a does not spread in the outer peripheral direction of the stator core 25 but is directly supplied to the coil end 26e.
  • the spout 72a is formed at a position that does not overlap the coil end 26e but overlaps the end of the stator core 25 when viewed in the radial direction.
  • the lubricating oil discharged in the radial direction from the oil hole 59 of the oil passage 50 has a lower flow velocity in the oil receiving chambers 71a and 71b, and then is more axial than the oil receiving chambers 71a and 71b. It rectifies
  • the lubricating oil is poured into the coil end 26e located at the uppermost position, whereby the lubricating oil is transmitted to other portions of the coil 26, and the lubricating oil is also transmitted to the lower coil 26. Falls down. Thereby, since the lubricating oil can be supplied to a portion of the coil 26 of the stator 24 that is not immersed in the lubricating oil, the coil 26 can be efficiently cooled.
  • the lubricating oil guide part 7 in this Embodiment contains the scattering prevention member 73 arrange
  • the scattering prevention member 73 is constituted by a plate-like member extending in the radial direction, for example.
  • the scattering prevention member 73 located on the inboard side is integrally formed with the oil pipe 51 so as to extend downward from the oil pipe 51, and the scattering prevention member 73 located on the outboard side extends downward from the oil pipe 52.
  • the oil pipe 52 is formed integrally. This facilitates positioning of the anti-scattering member 73 and suppresses an increase in the number of parts.
  • the scattering prevention member 73 is disposed within the axial width of each coil end 26e. Specifically, it is desirable that the scattering prevention member 73 overlaps the axially outer end portion of each coil end 26e when viewed in the radial direction. This prevents the lubricating oil flowing out from the spout 72a of the oil pouring path 72 from scattering over the coil end 26e. Further, it is desirable that the lower end position of the scattering prevention member 73 is above the upper end of the coil end 26e and below the upper end of the stator core 25.
  • the flow velocity and flow direction of the lubricating oil supplied to the coil end 26e of the stator 24 can be controlled. Therefore, the lubricating oil can be effectively supplied to the coil end 26e regardless of the rotational speed of the motor rotating shaft 22, that is, the discharge amount of the lubricating oil by the oil pump 43.
  • the lubricating oil is discharged from the oil hole 59 in the form of a beam, so a structure is adopted in which the lubricating oil is supplied directly from the oil hole 59 to the coil end 26e. Then, since the lubricating oil rebounds, the lubricating oil cannot be uniformly applied to the coil end 26e to be supplied.
  • the lubricating oil is discharged in the form of a beam from the oil hole 59, the lubricating oil is once received in the oil receiving chamber 71, and the lubricating oil is axially received in the oil pouring path 72. Since the rectification is performed, the lubricating oil can be supplied to the coil end 26e without waste. As a result, the coil 26 can be effectively cooled.
  • the oil passage 50 includes two oil pipes 51 and 52 .
  • the oil passage 50 is configured by a single oil pipe 58.
  • the fitting part 54 fitted to the thick part 29t is provided at the axial center position of the stator 24, and oil holes 59 are provided on both sides of the fitting part 54.
  • the oil pipe 58 is bolted to the other end face in the axial direction of the thick part 29t by a flange part 58a.
  • the lubricating oil supply structure according to the present embodiment is different from the first embodiment in that a lubricating oil guide portion 7A is provided instead of the above-described lubricating oil guide portion 7.
  • the lubricating oil supply structure includes an oil receiving chamber and a pouring channel.
  • the oil receiving chamber 71 ⁇ / b> A includes a fitting portion of the oil pipe 51. 54 and the fitting portion 55 of the oil pipe 52 are formed to have a larger diameter. That is, the through-hole 29h of the thick portion 29t is formed so that the central portion in the axial direction has a small diameter and both end portions in the axial direction have a large diameter.
  • This increases the cross-sectional area of the oil receiving chamber 71A and increases the amount of lubricating oil received, so that the flow velocity of the lubricating oil in the oil receiving chamber 71A can be sufficiently reduced.
  • Lubricating oil guide 7A does not include the scattering prevention member 73 described in the first embodiment, but includes a guide member 8 instead.
  • the guide member 8 includes a distribution member 81 for distributing the lubricating oil flowing out from the spout 72a (see FIG. 5 and the like) of the oil pouring path 72 to the plurality of coil ends 26e, and for preventing scattering of the lubricating oil.
  • the scattering prevention member 82 is integrally included.
  • FIG. 8 is a front view of the guide member 8 when viewed from the outside in the axial direction of the stator 24.
  • FIG. 9 is a top view of the guide member 8 as viewed from the IX direction of FIG.
  • FIG. 10 is a perspective view of the guide member 8.
  • FIG. 11 is a cross-sectional view showing the attachment state of the guide member 8.
  • the distribution member 81 includes a flange member 83 having a substantially U-shaped cross section and a plurality of holes 86 provided in the bottom surface 85 of the flange member 83.
  • the flange member 83 is formed in a substantially arc shape when viewed from the front.
  • the radius of the arc shape of the flange member 83 is substantially equal to the radius of the stator 24.
  • the central angle ⁇ of the arc shape of the flange member 83 is, for example, 60 ° or more and desirably 90 ° or less.
  • the flange member 83 is disposed so as to overlap, for example, the three coil ends 26e when viewed from the radially outer side (viewed from above).
  • holes 86 are provided at positions overlapping the coil ends 26e. It is desirable that a plurality of (for example, two) holes 86 are provided for one coil end 26e.
  • the bottom surface 85 of the eaves member 83 may not be an arc surface. As shown in the drawing, the center portion of the bottom surface 85 of the flange member 83 may be formed by a horizontal surface, and both end portions thereof may be formed by inclined surfaces.
  • One of the pair of rising portions 87 of the flange member 83 (hereinafter, referred to as the back side rising portion 87) abuts on the arc-shaped edge of the axial end surface of the stator core 25.
  • a central portion of the other rising portion 87 (hereinafter, referred to as a front side rising portion 87) of the flange member 83 is integrally formed with the scattering prevention member 82.
  • the leading end surface of the oil pouring path 72 and the rising portion 87 on the back side of the distribution member 81 are in contact with each other. That is, in the present embodiment, the spout 72a of the oil pouring path 72 is disposed on the boundary line between the stator core 25 and the coil end 26e.
  • the upper end position of the rising portion 87 on the back side is slightly above the stator core 25 and is within the thickness range of the member 72m that forms the oil pouring path 72. Therefore, the lubricating oil flowing out from the spout 72 a of the oil pouring path 72 can be surely poured into the distribution member 81.
  • the scattering prevention member 82 is a plate-like member extending in the radial direction (vertical direction) in the attached state.
  • the scattering prevention member 82 is formed flush with the rising portion 87 on the front side of the distribution member 81.
  • An arc-shaped notch 88 for receiving the oil pipe 51 or 52 is formed at the upper end of the scattering prevention member 82.
  • the guide member 8 further includes a plurality (three) of leg portions 84 connected to the lower end of the distribution member 81.
  • the leg portion 84 is a plate-like member formed flush with the rising portion 87 on the back side of the distribution member 81.
  • Each leg 84 is inserted into a slot 26s (FIG. 7) formed so as to penetrate in the radial direction between the axial end surface of the stator 24 and the coil end 26e.
  • the legs 84 are co-assembled when wound around the stator core 25.
  • the guide member 8 Since the guide member 8 is attached simply by inserting the plurality of legs 84 into the plurality of slots 26s formed on the axial end surface of the stator 24, the distribution member 81 and the scattering prevention member 82 can be easily installed. Can do.
  • the lubricating oil from the spout 72 a of the oil pouring path 72 flows down to the center of the eaves member 83 of the distribution member 81.
  • the lubricating oil that has flowed down to the central portion is divided into both the one side and the other side in the circumferential direction along the arc shape of the flange member 83. Since holes 86 are provided in the bottom surface 85 of each of the central portion and both end portions of the flange member 83, the lubricant oil flows down from the holes 86 in the process in which the lubricant oil flows over the flange member 83. As a result, the lubricating oil can be directly supplied to the plurality of coil ends 26e positioned relatively above.
  • the lubricating oil supply structure includes the distribution member 81, the coil 26 can be cooled more efficiently than in the first embodiment.
  • the scattering prevention member 82 is provided integrally with the distribution member 81, the lubricating oil that has hit the scattering prevention member 82 surely flows down to the distribution member 81. Therefore, an increase in the number of parts can be suppressed, and the lubricating oil can be led to the coil 26 without waste.
  • the oil passage 50 may be constituted by a single oil pipe 58 as shown in FIG.
  • FIG. 13 is a cross-sectional view schematically showing a main part of the lubricating oil supply structure according to Embodiment 3 of the present invention.
  • FIG. 14 is a diagram schematically showing the lubricant guide portion 7B in the third embodiment of the present invention.
  • the basic configuration of the lubricant guide 7B is substantially the same as that of the lubricant guide 7 of the first embodiment. Therefore, only differences from the first embodiment will be described below.
  • the lubricating oil supply structure according to the present embodiment includes one oil pipe 91 as the oil passage 50 in the motor chamber, similar to the oil pipe 58 of FIG. 6 shown in the first embodiment.
  • a plate-like scattering prevention member 73A is provided at the end portion on the outboard side of the oil pipe 91, but a plate-like scattering prevention member is not provided at the end portion on the inboard side of the oil pipe 91.
  • the inner end surface of the motor casing cover 29v as the rear cover has a scattering prevention shape.
  • the convex portion 93 provided on the inner end surface of the motor casing cover 29v functions as a scattering prevention member on the inboard side.
  • the convex portion 93 is formed at a position facing the pouring spout 72a of the oil pouring path 72 located on the inboard side in the axial direction.
  • the convex portion 93 is located below the connecting portion 92 of the motor casing cover 29v and is provided continuously therewith.
  • the connecting portion 92 is a portion having an opening for receiving the fitting portion 53 of the oil pipe 91.
  • the tip end position of the convex portion 93 is a position overlapping the end portion of the coil end 26e on the inboard side. With respect to the vertical position (radial position), a gap is provided between the convex portion 93 and the coil end 26e on the inboard side.
  • the scattering prevention member 73A integrally formed with the oil pipe 91 is provided only at the end portion on the outboard side of the oil pipe 91, so that the oil pipe 91 is thickened from the outboard side.
  • the scattering prevention member does not get in the way when inserted through the through hole 29h of the meat portion 29t. Therefore, even if the oil passage 50 is not composed of the two oil pipes 51 and 52 as shown in FIG. 3, the oil passage 50 can be realized by the single oil pipe 91 without impairing the scattering prevention function. it can.
  • the oil pipe 91 is fixed by the bolt 63 to the one axial end surface (outboard side end surface) of the thick portion 29t by the flange portion 91a.
  • the oil pipe 91 can be inserted into the thick part 29t from the outboard side through, for example, an opening (not shown) provided in the back surface portion 39b of the main body casing 39.
  • the oil pipe 91 is not provided with a large-diameter fitting portion (fitting portion 54 in FIG. 6) that fits into the through hole 29 h of the thick portion 29 t of the motor casing 29.
  • a partition portion 74 formed by processing the thick portion 29t is provided at the axial center position of the thick portion 29t.
  • the partition part 74 is comprised by the circular-arc-shaped or annular
  • the oil receiving chamber 71B is partitioned into two oil receiving chambers 71c and 71d in the axial direction via the partition portion 74. That is, in the present embodiment, the partition portion 74 suppresses the outflow of the lubricating oil from one oil receiving chamber to the other oil receiving chamber.
  • the position of the axial center of the partition portion 74 is offset vertically upward from the position of the axial center of the oil receiving chamber 71B.
  • the height of the part located in the downward side of the oil pipe 91 among the whole partition part 74 surrounding the outer periphery of the oil pipe 91 can be made high, the flow of the lubricating oil between the two oil receiving chambers 71c and 71d is effective. Can be prevented.
  • the diameter of the inner peripheral surface of the partition portion 74 is equal to or larger than the outer diameter of the fitting portion 53 of the oil pipe 91.
  • the oil receiving chambers 71 c and 71 d are formed in a tapered shape so that the cross-sectional area gradually increases toward the oil pouring path 72. In this case, there is no step in the vertical direction between the inner peripheral surfaces of the oil receiving chambers 71c and 71d and the inner peripheral surface of the oil pouring path 72, and these may be provided continuously.
  • the lateral width (length dimension along the vehicle longitudinal direction) of the plate-like scattering prevention member 73 ⁇ / b> A provided in the oil pipe 91 is larger than the lateral width (diameter) of the oil pouring path 72. .
  • both ends in the width direction of the scattering prevention member 73A may be bent inward. Thereby, it is possible to prevent the lubricating oil that has flowed out of the oil pouring path 72 from splashing further from the end in the width direction of the scattering preventing member 73A, and flowing out of the lubricating oil outside the coil end 26e.
  • the rigidity of the scattering prevention member 73A can be improved, the thickness of the scattering prevention member 73A can be reduced, and the weight can be reduced.
  • FIG. 15 is a cross-sectional view schematically showing a main part of the lubricating oil supply structure according to Embodiment 4 of the present invention.
  • FIG. 16 is a diagram schematically showing a lubricant guide portion 7C in the fourth embodiment of the present invention.
  • the basic configuration of the lubricant guide 7C is substantially the same as the lubricant guide 7A of the second embodiment. Therefore, only differences from the second embodiment will be described below.
  • the lubricating oil supply structure according to the present embodiment includes one oil pipe 91A as the oil passage 50 in the motor chamber, similarly to the oil pipe 58 of FIG. 12 shown in the second embodiment.
  • the oil pipe 91A has substantially the same configuration as the oil pipe 91 of the third embodiment.
  • the lubricating oil guide 7C includes a guide member 8A located on the outboard side and a guide member 8B located on the inboard side.
  • the guidance member 8A on the outboard side has only the distribution member 81 shown in the second embodiment, and does not have the scattering prevention member 82 (see FIG. 11 and the like) shown in the second embodiment.
  • the guide member 8B on the inboard side includes the distribution member 81 and the scattering prevention member 82A formed integrally therewith, like the guide member 8 of the second embodiment.
  • the guide member 8A on the outboard side does not include the scattering prevention member, but instead, the oil pipe 91A is provided only on the outboard side in the same manner as the oil pipe 91 shown in the third embodiment. It has integrally the shape scattering prevention member 73B. Thereby, also in the present embodiment, the scattering prevention member 73B is provided only at the end portion on the outboard side of the oil pipe 91A, so that the oil pipe 91A is inserted from the outboard side into the through hole 29h of the thick portion 29t. When doing so, the anti-scattering member does not get in the way.
  • the oil passage 50 can be realized by the single oil pipe 91A.
  • the scattering prevention member 73B is arranged directly above the rising portion 87 on the front side of the distribution member 81 that constitutes the guide member 8A, and therefore has a shorter vertical length than the scattering prevention member 73A of the third embodiment.
  • the scattering prevention member 82A of the guide member 8B is integrally formed with the rising portion 87 on the front side of the distribution member 81 as in the second embodiment.
  • the fitting part 53 located at the inboard side end of the oil pipe 91A is larger than the outer diameter of the oil pipe 91A main body. This is because it is necessary to form an annular groove on the outer peripheral surface of the fitting portion 53 into which the O-ring 56 as a seal member is fitted.
  • the distance L2 between the scattering prevention member 82A and the connection portion 92 of the motor casing cover 29v is set to be not less than the axial dimension L1 of the fitting portion 53 of the oil pipe 91A.
  • the scattering prevention member 82A in the attached state, can be arranged so that the upper end portion of the scattering prevention member 82A overlaps the fitting portion 53 of the oil pipe 91A when viewed in the axial direction. it can. Thereby, it becomes possible to suppress the leakage of the lubricating oil from the gap between the scattering prevention member 82A and the oil pipe 91A as much as possible.
  • the oil passage 50 has only the oil hole 59 provided at a position overlapping with the stator core 25.
  • the oil passage 50 also has an oil hole at a position not overlapping with the stator core 25. Also good.
  • oil receiving chamber 71 is formed in the motor casing 29, it may be constituted by another member that can be attached to the motor casing 29.
  • the oil pouring path 72 is formed by the arc-shaped member 72m, similarly to the oil receiving chamber 71, it may be formed by a cylindrical member.
  • the cross-sectional shape of the oil receiving chamber 71 is circular (perfect circle), it is not limited.
  • the oil receiving chamber 71 may be disposed so as to surround the outer periphery of the oil passage 50, and the cross-sectional shape of the oil receiving chamber 71 may be another shape such as an ellipse or a polygon.
  • the cross-sectional shape of the oil pouring path 72 is a semicircular shape, it is not limited. It is sufficient that the lubricating oil can flow along the axial direction (in a direction parallel to the oil passage 50) at a position below the oil pouring path 72 and the oil receiving chamber 71.
  • the cross-sectional shape of the oil pouring path 72 is, for example, V Other shapes such as a letter shape or a U shape may be used.
  • the oil pouring path 72 may not be provided.
  • a lubricating oil pouring path to the coil end 26 e is formed at the downstream end of the oil receiving chamber 71.
  • FIG. 17 is a cross-sectional view schematically showing a lubricating oil supply structure according to Embodiment 5 of the present invention.
  • the in-wheel motor drive device 1A is passed through the axis O, the axis M, and the oil passage 50 by a predetermined amount. It is the longitudinal cross-sectional view cut
  • FIG. 18 schematically shows a state in which the internal structure of the speed reduction unit 31 of the in-wheel motor drive device 1A is viewed from the outboard side.
  • the in-wheel motor drive device 1A disposed in the inner space of the wheel wheel W is connected to a vehicle body (not shown) via the suspension device 100 as shown in FIG.
  • the suspension device 100 is, for example, a strut suspension device, and includes a lower arm 101 extending in the vehicle width direction and a damper 102 disposed above the lower arm 101 and extending in the vertical direction.
  • the main part of the lubricating oil supply structure according to the present embodiment is shown in FIG.
  • the lubricating oil supply structure according to the present embodiment includes a lubricating oil guide portion 7 ⁇ / b> D that guides the lubricating oil discharged from the oil hole 59 of the oil passage 50 to the coil end 26 e of the stator 24.
  • the oil passage 50 is constituted by a single oil pipe 91B disposed so as to penetrate the thick portion 29t of the motor casing 29 and the back portion 39b of the main body casing 39 in the axial direction.
  • the back surface portion 39b of the main body casing 39 functions as a partition wall that partitions the motor chamber S1 (motor unit 21) in the motor casing 29 and the deceleration chamber S2 (deceleration unit 31) in the main body casing 39 in the axial direction. Therefore, in the following description, the back portion 39b of the main body casing 39 is referred to as a partition wall 39b of the casing 10.
  • the lubricating oil is supplied to both the motor chamber S1 and the speed reduction chamber S2 by one oil pipe 91B. Can do.
  • FIG. 20 is a diagram showing an example of the internal structure of the casing 10 on the deceleration chamber S2 side, and FIG. 20 schematically shows an end face on the outboard side of the partition wall 39b.
  • 20A is a front view
  • FIG. 20B is a perspective view.
  • FIG. 20 shows a state where the flat wall portion constituting the front portion 39f of the main body casing 39 is removed.
  • FIG. 21 is a perspective view of a vertical cross-sectional structure of the upper part of the motor casing 29 (including the motor casing cover 29v) through which the oil pipe 91B is inserted, as viewed from the speed reduction chamber S2.
  • the oil pipe 91B is supported by the casing 10 at both ends.
  • One end (inboard side end portion) of the oil pipe 91B is fitted to the connection portion 92 of the motor casing cover 29v in the fitting portion 53, as in the above embodiments.
  • the other end (outboard side end) of the oil pipe 91B is bolted to the partition wall 39b of the casing 10.
  • the partition wall 39b of the casing 10 is provided with an opening 39h through which the oil pipe 91B is inserted.
  • a mounting bracket (bracket) 91t is connected to the outer peripheral surface of the oil pipe 91B located on the deceleration chamber S2 side in the installed state by welding or the like.
  • the mounting bracket 91t includes a plate-like portion extending in the radial direction orthogonal to the oil pipe 91B, and has a through-hole (not shown) penetrating in the plate thickness direction in the plate-like portion.
  • a female screw hole 39i is provided in the vicinity of the opening 39h on the end surface on the outboard side of the partition wall 39b.
  • the other end side (outboard side end portion) of the oil pipe 91B is inserted into the through hole of the mounting bracket 91t through the shaft portion of the bolt 64 from the outboard side and screwed into the female screw hole 39i. Fixed to the outboard side end face.
  • the oil pipe 91B in the present embodiment, after the assembly of the motor unit 21 is completed at the time of manufacturing the in-wheel motor drive device 1A (as shown in FIGS. 18 and 20, the main body casing 39).
  • the oil pipe 91B can be easily attached from the speed reduction chamber S2 side (in the state where the flat wall portion constituting the front portion 39f is removed). Specifically, the oil pipe 91B is attached to the casing 10 in the following procedure.
  • the oil pipe 91 ⁇ / b> B is inserted into the opening 39 h of the partition wall 39 b of the casing 10 from the outboard side so that the fitting portion 53 is at the head.
  • the fitting part 53 passes through the through hole 29h of the thick part 29t and reaches the motor casing cover 29v, the fitting part 53 is fitted into the connection part 92 of the motor casing cover 29v.
  • the inboard side end portion of the oil pipe 91 ⁇ / b> B is fixed by fitting the O-ring 56 provided on the outer periphery of the fitting portion 53 and the connection portion 92.
  • the mounting bracket 91t connected to the oil pipe 91B is fixed to the end face on the outboard side of the partition wall 39b with the bolt 64.
  • the end portion on the outboard side of the oil pipe 91B is bolted to the partition wall 39b.
  • the lubricating oil can be sent not only to the motor chamber S1 but also to the deceleration chamber S2 with one oil pipe 91B, so the number of parts can be reduced. In addition, the manufacturing cost can be reduced. Further, as shown in FIG. 21, both end portions in the axial direction of the oil pipe 91B are supported by the casing 10 by the O-ring 56 and the bolt 64, so that the oil pipe 91B can be made difficult to tilt.
  • FIG. 22 is a diagram schematically showing the lubricating oil guide portion 7D, and is a view of the upper cross section structure of the motor casing 29 (thick portion 29t) and the oil pipe 91B as viewed obliquely from above.
  • FIG. 23 is a diagram schematically showing the lubricating oil guide portion 7D, and is a diagram showing the cross-sectional structure of the upper portion (thick portion 29t) of the motor casing 29 as viewed from obliquely above with the oil pipe 91B removed. is there.
  • FIG. 24 is a view of the motor chamber S1 as seen from the inboard side with the motor casing cover 29v removed.
  • FIG. 25 is a diagram showing an example of the internal structure of the casing 10 on the motor chamber S1 side.
  • FIG. 25 schematically shows the inboard-side end surfaces of the partition wall portion 39b and the thick portion 29t.
  • FIG. 25A is a front view
  • FIG. 25B is a perspective view.
  • the lubricating oil guide 7D includes an oil receiving chamber 71C that receives lubricating oil discharged from the oil hole 59 of the oil pipe 91B located above the stator core 25.
  • the oil receiving chamber 71C is divided into two oil receiving chambers 71e and 71f in the thick portion 29t at the top of the motor casing 29 with the partition portion 74A as a boundary.
  • the partition portion 74A is configured by an arc-shaped or annular convex portion protruding from the inner peripheral surface of the through hole 29h of the thick portion 29t.
  • the convex portion as the partitioning portion 74A only needs to be disposed at least below the axial center height of the oil pipe 91B.
  • the inner diameter dimension (minimum dimension) of the partition portion 74A is larger than the outer diameter dimension of the fitting portion 53 of the oil pipe 91B.
  • At least one oil hole 59 is provided on the outboard side and the inboard side from the axial position of the partition portion 74A within the axial width of the stator core 25.
  • the lubricating oil is discharged from the oil hole 59 to the respective oil receiving chambers 71e and 71f.
  • the partition portion 74A is provided between the oil receiving chambers 71e and 71f, it is possible to prevent the lubricating oil received in each oil receiving chamber 71e and 71f from entering the other oil receiving chamber. Accordingly, it is possible to prevent a large amount of lubricating oil from flowing only on one side of the coil ends 26e disposed on both sides in the axial direction of the stator 24 (a supply amount of the lubricating oil is not uniform).
  • the lubricating oil guide 7D communicates with the oil receiving chamber 71e on the outboard side and extends along the axial direction 72A, and with the oil receiving chamber 71f on the inboard side and extends along the axial direction. And a pouring channel 72B.
  • the shape of oil pouring paths 72A and 72B in the present embodiment is not a semicircular shape, but may be a valley shape having a substantially flat bottom surface 72f as shown in FIG. Thereby, in the oil pouring paths 72A and 72B, the flow direction of the lubricating oil can be converged in the axial direction more effectively.
  • the axial position of the partition portion 74 ⁇ / b> A is shifted to the outboard side from the center position LA of the stator 24.
  • the axial length of at least one of the oil receiving chamber 71e and the oil pouring path 72A on the outboard side is shorter than the axial length of the oil receiving chamber 71f and the oil pouring path 72B on the inboard side.
  • the axial lengths of both the oil receiving chamber 71e on the outboard side and the oil pouring path 72A are shorter than the axial lengths of the oil receiving chamber 71f and the oil pouring path 72B on the inboard side.
  • the oil receiving chamber 71f on the inboard side gradually increases in cross-sectional area toward the oil pouring path 72B (as it goes to the inboard side), as in the third embodiment.
  • it is formed in a tapered shape. That is, the oil receiving chamber 71f on the inboard side is inclined along the axial direction (relative to the axis M) so that the lower end height of the inboard oil receiving chamber 71f becomes lower as the distance from the partition portion 74A increases.
  • the oil receiving chamber 71e on the outboard side may also be inclined along the axial direction (relative to the axis M) so that the lower end height of the oil receiving chamber 71e becomes lower as the distance from the partition portion 74A increases.
  • the oil receiving chamber 71f on the inboard side has a larger gradient (inclination angle) than the oil receiving chamber 71e on the outboard side.
  • the oil pouring path 72B on the inboard side has a larger gradient (inclination angle) than the oil pouring path 72A on the outboard side.
  • the oil receiving chamber 71f or the oil pouring path 72B on the inboard side is inclined so that the lubricating oil can easily flow outward in the axial direction.
  • the gradient of at least one of the oil receiving chamber 71e on the outboard side and the oil pouring path 72A may be a so-called draft angle.
  • the inclined surface that is inclined along the axial direction is not limited to a smooth inclined surface (tapered surface). May be formed by a wavy surface configured to allow the lubricating oil to flow toward the surface or a surface having a plurality of steps.
  • the inclination angle of the oil receiving chamber 71f (71e) and the inclination angle of the oil pouring path 72B (72A) may be determined in consideration of the camber angle when the in-wheel motor drive device 1A is attached to the vehicle body.
  • the oil pouring path 72A is faced.
  • An oil hole 59 may be disposed at the position. That is, the oil pouring path 72A may also have a function of receiving oil discharged from the oil hole 59 of the oil pipe 91B.
  • the lubricant guide 7D includes a pair of distribution members 81A and 81A for distributing the lubricant flowing out from the oil pouring paths 72A and 72B to the plurality of coil ends 26e.
  • the lubricating oil guide 7D also prevents scattering of the lubricating oil flowing out from the oil pouring path 72A on the outboard side and preventing scattering of lubricating oil flowing out from the oil pouring path 72B on the inboard side.
  • an anti-scattering member 73D is an anti-scattering member 73D.
  • the distribution member 81A includes a flange member 83A and a plurality of holes 86 provided in the bottom surface 85 of the flange member 83A.
  • the flange member 83 ⁇ / b> A does not have a rising portion that contacts the arcuate edge 25 a of the axial end surface of the stator core 25, and the bottom surface 85 of the flange member 83 ⁇ / b> A is an axial end surface of the stator core 25. It is in contact with the edge portion 25a.
  • the plurality of leg portions 84 integrally connected to the flange member 83A are inserted into the plurality of slots 26s formed on the axial end surface of the stator 24, respectively. Attached by.
  • the arcuate scissors 83A as viewed in the axial direction is on or near a virtual line LB connecting the axis C of the oil pipe 91B (oil passage 50) and the axis M of the motor rotating shaft 22.
  • a partition wall 89 may be provided at the center of the flange member 83A.
  • the partition wall 89 is erected on the bottom surface 85 of the flange member 83A so as to close a space between the edge 25e of the axial end surface of the stator core 25 and the rising portion 87 of the flange member 83A.
  • the partition wall 89 causes the vehicle to Lubricating oil can be distributed in the front-rear direction.
  • the lubricating oil can be appropriately distributed to the plurality of coil ends 26e.
  • the anti-scattering member 73C on the outboard side is composed of a plate-like member connected to the oil pipe 91B by welding or the like, similar to the anti-scattering member 73B of the fourth embodiment.
  • the scattering prevention member 73C is located above the distribution member 81A, and is disposed so as to face the axial end (pour spout) of the oil pouring path 72A in the axial direction.
  • the scattering prevention member 73C may be disposed closer to the stator core 25 (inboard side) than the rising portion 87 of the distribution member 81A.
  • the scattering prevention member 73C has a shape and a size that can pass through the opening 39h provided in the partition wall 39b while being fixed to the oil pipe 91B. Further, the anti-scattering member 73C may be integrally formed with the mounting bracket 91t described above.
  • the inboard-side scattering prevention member 73D is configured by a convex portion 93 provided on the motor casing cover 29v, as in the third embodiment. That is, the anti-scattering member 73D is provided on the inner end surface of the motor casing cover 29v so as to continue below the connection portion 92.
  • the lubricant can be supplied from above to the coil ends 26e on both sides in the axial direction with a simple structure. Can be cooled.
  • the lubricating oil supplied to the coil end 26e also contributes to the lubrication of the rolling bearings 27 and 28 that rotatably support the motor rotating shaft 22.
  • a resolver (rotation sensor) 68 for detecting the rotation of the motor rotation shaft 22 is provided at the inboard side end of the motor rotation shaft 22, the inboard-side rolling bearing 28 is provided.
  • the motor casing cover 29v may be configured such that the supplied lubricating oil is guided to the sensor chamber S3.
  • the sensor chamber S3 is a space in which the resolver 68 is accommodated.
  • FIG. 26 is a perspective view of the motor casing cover 29v as viewed from the outboard side (from the motor chamber S1 side)
  • FIG. 27 is a front view of the motor casing cover 29v as viewed from the inboard side
  • FIG. 28 is a longitudinal sectional view schematically showing the sensor chamber S3 provided in the motor casing cover 29v.
  • the motor casing cover 29v has a cylindrical portion 66 into which the rolling bearing 28 and the resolver 68 are fitted coaxially. In the cylindrical portion 66, the resolver 68 is disposed on the inboard side with respect to the rolling bearing 28.
  • the motor casing cover 29v is provided with a communication hole 69 for drawing a signal line (not shown) of the resolver 68 from the sensor chamber S3 to the motor chamber S1.
  • the communication hole 69 is located below the axis M.
  • a discharge passage 67 is provided that penetrates from the motor chamber S1 to the sensor chamber S3 in the axial direction. Accordingly, the lubricating oil that has lubricated the rolling bearing 28 is discharged to the sensor chamber S3 through the discharge path 67. The lubricating oil discharged to the sensor chamber S3 flows again through the communication hole 69 to the motor chamber S1. In this way, the lubricating oil that lubricates the rolling bearing 28 bypasses the sensor chamber S3 and returns from the communication hole 69 to the motor chamber S1, so that the lubricating oil can hardly be applied to the rotor 23. Therefore, the rotational resistance of the rotor 23 can be reduced.
  • the lubricating oil used for cooling the stator 24 passes from the motor chamber S1 through the opening 39j (FIGS. 18 and 19) provided in the partition wall portion 39b. It returns to the oil tank 40 provided in S2.
  • the opening 39j of the partition wall 39b is located below the axis M and functions as an oil return path.
  • the opening 39j as an oil return path is provided at a position overlapping the stator 24 in the axial direction. That is, it is desirable that the opening 39j is located inside the outer circumference circle (indicated by a broken line in FIG. 18) of the stator core 25. In this case, as shown in FIG. 18, when the partition wall 39b is viewed from the inboard side, the lower end of the stator 24 (the coil end 26e and the edge 25e of the axial end surface of the stator core 25) is exposed from the opening 39j.
  • the lubricating oil easily returns to the oil tank 40, so that the lubricating oil can be circulated efficiently even if the amount of the lubricating oil enclosed in the casing 10 is reduced. Further, by reducing the amount of lubricating oil, it is possible to reduce the weight of the in-wheel motor drive device 1A.

Landscapes

  • Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)
  • Motor Or Generator Cooling System (AREA)

Abstract

Cette structure d'alimentation en lubrifiant comprend : un trajet d'huile (50) qui est disposé le long de la direction axiale d'un moteur au-dessus d'un stator (24), et qui a au moins un trou d'huile (59) à travers lequel le lubrifiant pompé par une pompe à huile est évacué dans la direction radiale; et une partie de guidage de lubrifiant (7) qui guide le lubrifiant évacué du trou d'huile (59) jusqu'à une extrémité de bobine (26e) du stator. La partie de guidage de lubrifiant (7) comprend une chambre de réception d'huile (71) qui reçoit le lubrifiant évacué du trou d'huile (59).
PCT/JP2019/004538 2018-02-08 2019-02-08 Structure d'alimentation en lubrifiant et dispositif d'entraînement de moteur-roue WO2019156196A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201980012074.8A CN111699618A (zh) 2018-02-08 2019-02-08 润滑油的供给结构及轮毂电动机驱动装置

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2018-020690 2018-02-08
JP2018020690 2018-02-08
JP2019020232A JP2019140906A (ja) 2018-02-08 2019-02-07 潤滑油の供給構造、および、インホイールモータ駆動装置
JP2019-020232 2019-02-07

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WO2019156196A1 true WO2019156196A1 (fr) 2019-08-15

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114552891A (zh) * 2020-11-19 2022-05-27 日本电产株式会社 旋转电机和驱动装置
US20220281310A1 (en) * 2021-03-08 2022-09-08 Nidec Corporation Drive device
US11742720B2 (en) * 2019-08-30 2023-08-29 Hyundai Motor Company Motor provided with cooling system

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013090454A (ja) * 2011-10-18 2013-05-13 Toyota Motor Corp 車両用回転電機の冷却装置
JP2014135817A (ja) * 2013-01-09 2014-07-24 Toyota Industries Corp 回転電機
JP2016208722A (ja) * 2015-04-24 2016-12-08 日産自動車株式会社 駆動ユニット
JP2017192224A (ja) * 2016-04-14 2017-10-19 Ntn株式会社 車両用駆動装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013090454A (ja) * 2011-10-18 2013-05-13 Toyota Motor Corp 車両用回転電機の冷却装置
JP2014135817A (ja) * 2013-01-09 2014-07-24 Toyota Industries Corp 回転電機
JP2016208722A (ja) * 2015-04-24 2016-12-08 日産自動車株式会社 駆動ユニット
JP2017192224A (ja) * 2016-04-14 2017-10-19 Ntn株式会社 車両用駆動装置

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11742720B2 (en) * 2019-08-30 2023-08-29 Hyundai Motor Company Motor provided with cooling system
CN114552891A (zh) * 2020-11-19 2022-05-27 日本电产株式会社 旋转电机和驱动装置
CN114552891B (zh) * 2020-11-19 2024-04-16 日本电产株式会社 旋转电机和驱动装置
US20220281310A1 (en) * 2021-03-08 2022-09-08 Nidec Corporation Drive device

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