WO2022180875A1 - Rotating electric machine and drive device - Google Patents

Rotating electric machine and drive device Download PDF

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Publication number
WO2022180875A1
WO2022180875A1 PCT/JP2021/022349 JP2021022349W WO2022180875A1 WO 2022180875 A1 WO2022180875 A1 WO 2022180875A1 JP 2021022349 W JP2021022349 W JP 2021022349W WO 2022180875 A1 WO2022180875 A1 WO 2022180875A1
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WO
WIPO (PCT)
Prior art keywords
shaft
electric machine
threaded portion
rotor
rotating
Prior art date
Application number
PCT/JP2021/022349
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French (fr)
Japanese (ja)
Inventor
亮磨 佐々木
茂 前田
Original Assignee
日本電産株式会社
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Filing date
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Application filed by 日本電産株式会社 filed Critical 日本電産株式会社
Publication of WO2022180875A1 publication Critical patent/WO2022180875A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • 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

Definitions

  • the present invention relates to a rotating electric machine and a driving device.
  • An electric motor that includes a rotor having a rotating shaft and a stator in which the rotor is arranged and that rotates the rotor by a rotating magnetic field (see, for example, Patent Document 1).
  • the rotor of the electric motor described in Patent Document 1 has a hollow rotating shaft. By circulating a coolant such as cooling oil in the rotating shaft, it is possible to suppress the temperature rise of the rotor.
  • An object of the present invention is to provide a rotating electric machine and a driving device that improve cooling efficiency for the rotor and stator.
  • a rotor having a shaft in which a coolant can flow and rotatable around the shaft; a stator positioned radially outward of the rotor,
  • the shaft is a cylindrical shaft body having a first threaded portion provided on an inner peripheral surface and a plurality of first side holes penetrating in a radial direction;
  • a cylindrical body having a second threaded portion provided on the outer peripheral surface and a plurality of second side holes penetrating in the radial direction, By rotating the second threaded portion to fit the first threaded portion, the plurality of second side holes are aligned with the plurality of second side holes in a mounting state in which the cylindrical body is mounted on one side of the shaft body in the axial direction.
  • the plurality of first side holes and the plurality of second side holes are connected via between the first screw portion and the second screw portion, and function as a flow path through which the refrigerant can pass.
  • One aspect of the drive device of the present invention is a drive device that is mounted on a vehicle and rotates an axle, The rotating electrical machine described above; a transmission device that is connected to the rotating electrical machine and that transmits rotation of the rotor to the axle; a housing that accommodates the rotating electric machine and the transmission device; and a coolant passage provided in the housing for supplying a coolant to the shaft and the stator of the rotating electric machine.
  • cooling efficiency for the rotor and stator is improved.
  • FIG. 1 is a schematic configuration diagram schematically showing a driving device according to one embodiment.
  • FIG. 2 is a longitudinal sectional view of a shaft that the rotor has.
  • FIG. 3 is an enlarged vertical cross-sectional view of a shaft that the rotor has.
  • FIG. 4 is an enlarged view of a region [A] surrounded by a dashed line in FIG.
  • FIG. 5 is a longitudinal sectional view showing the positional relationship between the shaft body and the cylindrical body in the rotor.
  • FIG. 6 is a longitudinal sectional view showing the positional relationship between the shaft body and the cylindrical body in the rotor.
  • FIG. 7 is a vertical cross-sectional perspective view of the shaft body.
  • FIG. 8 is a vertical cross-sectional perspective view of a cylindrical body.
  • the central axis J shown in the drawing as appropriate is a virtual axis extending in a direction intersecting the vertical direction.
  • the direction parallel to the central axis J is simply referred to as the "axial direction”
  • the radial direction about the central axis J is simply referred to as the "radial direction”
  • the circumferential direction about the central axis J is sometimes simply referred to as the "circumferential direction”.
  • the vertical direction, the horizontal direction, the upper side, and the lower side are names for simply explaining the relative positional relationship of each part, and the actual positional relationship, etc. are the positions indicated by these names. A layout relationship other than the relationship may be used.
  • the left side is called “upstream side” and the right side is called “downstream side”.
  • the “upstream side” corresponds to “one side in the axial (central axis J) direction”
  • the “downstream side” corresponds to “the other side in the axial (central axis J) direction”.
  • a driving device 100 of the present embodiment shown in FIG. 1 is mounted on a vehicle and rotates an axle 64 .
  • a vehicle in which drive device 100 is mounted is a vehicle using a motor as a power source, such as a hybrid vehicle (HEV), a plug-in hybrid vehicle (PHV), an electric vehicle (EV), or the like.
  • HEV hybrid vehicle
  • PHY plug-in hybrid vehicle
  • EV electric vehicle
  • drive device 100 includes rotary electric machine 10 , housing 80 , transmission device 60 , and coolant channel 90 .
  • the rotary electric machine 10 includes a rotor 30 rotatable around a central axis (axis) J and a stator 40 located radially outside the rotor 30 .
  • the housing 80 accommodates the rotary electric machine 10 and the transmission device 60 .
  • Housing 80 has a motor housing 81 and a gear housing 82 .
  • Motor housing 81 is a housing that accommodates rotor 30 and stator 40 therein.
  • the motor housing 81 is connected to the right side of the gear housing 82 .
  • the motor housing 81 has a peripheral wall portion 81a, a partition wall portion 81b, and a lid portion 81c.
  • the peripheral wall portion 81a and the partition wall portion 81b are, for example, part of the same single member.
  • the lid portion 81c is separate from, for example, the peripheral wall portion 81a and the partition wall portion 81b.
  • the peripheral wall portion 81a has a tubular shape surrounding the central axis J and opening on the right side.
  • the partition wall portion 81b is connected to the left end portion of the peripheral wall portion 81a.
  • the partition wall portion 81b separates the interior of the motor housing 81 and the interior of the gear housing 82 in the axial direction.
  • the partition wall portion 81 b has a partition wall opening 81 d that connects the inside of the motor housing 81 and the inside of the gear housing 82 .
  • a bearing 34 is held in the partition portion 81b.
  • the lid portion 81c is fixed to the right end of the peripheral wall portion 81a.
  • the lid portion 81c closes the opening on the right side of the peripheral wall portion 81a.
  • a bearing 35 is held in the lid portion 81c.
  • the gear housing 82 accommodates the reduction gear 62 and the differential gear 63 of the transmission device 60 and the oil O inside.
  • the oil O is stored in the lower area inside the gear housing 82 .
  • the oil O circulates inside the coolant flow path 90 .
  • Oil O is used as a coolant for cooling rotating electric machine 10 .
  • the oil O is used as a lubricating oil for the reduction gear 62 and the differential gear 63 .
  • the oil O for example, it is preferable to use an oil equivalent to automatic transmission fluid (ATF), which has a relatively low viscosity, in order to function as a refrigerant and a lubricating oil.
  • ATF automatic transmission fluid
  • the transmission device 60 is connected to the rotating electric machine 10 and transmits the rotation of the rotor 30 to the axle 64 of the vehicle.
  • a transmission device 60 of the present embodiment has a reduction gear 62 connected to the rotating electric machine 10 and a differential gear 63 connected to the reduction gear 62 .
  • the differential gear 63 has a ring gear 63a. Torque output from the rotary electric machine 10 is transmitted to the ring gear 63 a via the reduction gear 62 .
  • a lower end portion of the ring gear 63 a is immersed in the oil O stored in the gear housing 82 .
  • the oil O is scooped up by the rotation of the ring gear 63a.
  • the scooped-up oil O is supplied as lubricating oil to, for example, the reduction gear 62 and the differential gear 63 .
  • the rotating electrical machine 10 is a part that drives the driving device 100 .
  • the rotating electrical machine 10 is positioned, for example, on the right side of the transmission device 60 .
  • the rotating electric machine 10 is a motor.
  • Torque of rotor 30 of rotating electric machine 10 is transmitted to transmission device 60 .
  • the rotor 30 has a shaft 1 extending axially around a central axis J and a rotor body 32 fixed to the shaft 1 .
  • the rotor main body 32 is composed of, for example, a plurality of rotor core portions fixed to the outer peripheral surface of the shaft 1 and arranged in the axial direction, and magnets and the like held in each rotor core portion.
  • the shaft 1 is rotatable around the central axis J. Thereby, the rotor 30 can rotate around the shaft 1 .
  • the shaft 1 is rotatably supported by bearings 34 and 35 .
  • the shaft 1 is a hollow shaft.
  • the shaft 1 has a cylindrical shape through which oil O as a coolant can flow.
  • the shaft 1 extends across the interior of the motor housing 81 and the interior of the gear housing 82 .
  • the left end of the shaft 1 protrudes inside the gear housing 82 .
  • a reduction gear 62 is connected to the left end of the shaft 1 .
  • the stator 40 is positioned radially outwardly of the rotor 30 with a gap therebetween.
  • the stator 40 surrounds the rotor 30 from the radially outer side along the entire circumference.
  • the stator 40 is fixed inside the motor housing 81 .
  • Stator 40 has a stator core 41 and a coil assembly 42 .
  • the stator core 41 has an annular shape surrounding the central axis J of the rotary electric machine 10 .
  • the stator core 41 is configured, for example, by laminating a plurality of plate members such as electromagnetic steel plates in the axial direction.
  • the coil assembly 42 has a plurality of coils 42c attached to the stator core 41 along the circumferential direction.
  • the plurality of coils 42c are attached to respective teeth (not shown) of the stator core 41 via insulators (not shown).
  • a plurality of coils 42c are arranged along the circumferential direction.
  • Coil 42c has a portion protruding from stator core 41 in the axial direction.
  • the coolant channel 90 is provided inside the housing 80 . Oil O as a coolant flows through the coolant channel 90 .
  • the coolant flow path 90 is provided across the inside of the motor housing 81 and the inside of the gear housing 82 .
  • the coolant flow path 90 is a path through which the oil O stored in the gear housing 82 is supplied to the rotating electric machine 10 in the motor housing 81 and returns to the gear housing 82 again.
  • a pump 71 and a cooler 72 are provided in the coolant channel 90 .
  • the coolant channel 90 includes a first channel portion 91 , a second channel portion 92 , a third channel portion 93 , a stator coolant supply portion 50 , a shaft channel portion 95 , and a connection channel portion 94 . , a radial channel portion 96 , an axial channel portion 98 , and a guide channel portion 97 .
  • the first flow path part 91, the second flow path part 92, and the third flow path part 93 are provided on the wall of the gear housing 82, for example.
  • the first flow path portion 91 connects a portion of the gear housing 82 where the oil O is stored and the pump 71 .
  • the second channel portion 92 connects the pump 71 and the cooler 72 .
  • the third flow path portion 93 connects the cooler 72 and the stator coolant supply portion 50 .
  • the third flow path portion 93 is connected to the left end portion of the stator coolant supply portion 50 , that is, the upstream portion of the stator coolant supply portion 50 .
  • a stator coolant supply unit 50 supplies oil O to the stator 40 .
  • the stator coolant supply portion 50 has a tubular shape extending in the axial direction.
  • the stator coolant supply portion 50 is a pipe extending in the axial direction. Both axial end portions of the stator coolant supply portion 50 are supported by the motor housing 81 .
  • a left end portion of the stator coolant supply portion 50 is supported by, for example, the partition portion 81b.
  • a right end portion of the stator coolant supply portion 50 is supported by, for example, the lid portion 81c.
  • the stator coolant supply portion 50 is positioned radially outward of the stator 40 .
  • the stator coolant supply section 50 is positioned above the stator 40 .
  • the stator coolant supply section 50 has a supply port 50a for supplying the oil O to the stator 40 .
  • the supply port 50 a is an injection port that injects part of the oil O that has flowed into the stator coolant supply portion 50 to the outside of the stator coolant supply portion 50 .
  • the supply port 50a is formed by a hole penetrating the wall portion of the stator coolant supply portion 50 from the inner peripheral surface to the outer peripheral surface.
  • a plurality of supply ports 50 a are provided in the stator coolant supply portion 50 .
  • the plurality of supply ports 50a are spaced apart from each other, for example, in the axial direction or the circumferential direction.
  • the shaft channel portion 95 is arranged inside the shaft 1 . Thereby, the oil O can be supplied into the shaft 1 .
  • the connection channel portion 94 connects the inside of the stator coolant supply portion 50 and the inside of the shaft 1 .
  • the connection channel portion 94 connects the right end portion of the stator coolant supply portion 50 , that is, the downstream portion, and the right end portion of the shaft channel portion 95 , that is, the upstream portion.
  • the connection channel portion 94 is provided, for example, in the lid portion 81c. According to this embodiment, it is possible to stably cool the stator 40 and the rotor 30 while simplifying the configuration of the coolant flow path 90 .
  • the axial channel portion 98 connects the radial channel portion 96 and the guide channel portion 97 .
  • the axial channel portion 98 is arranged over the interior of the plurality of rotor core portions.
  • the oil O stored in the gear housing 82 is sucked up through the first flow passage portion 91 and then through the second flow passage portion 92 into the cooler 72. flow into The oil O that has flowed into the cooler 72 is cooled in the cooler 72 and then flows through the third flow path portion 93 to the stator coolant supply portion 50 . A portion of the oil O that has flowed into the stator coolant supply portion 50 is injected from the supply port 50 a and supplied to the stator 40 . Another part of the oil O that has flowed into the stator coolant supply portion 50 flows into the shaft flow channel portion 95 through the connection flow channel portion 94 .
  • Another part of the oil O that has flowed into the shaft flow path portion 95 is discharged into the gear housing 82 through the left opening of the shaft 1 and is stored in the gear housing 82 again.
  • the oil O supplied to the stator 40 from the supply port 50 a takes heat from the stator 40
  • the oil O supplied to the rotor 30 and stator 40 from within the shaft 1 takes heat from the rotor 30 and stator 40 .
  • the oil O that has cooled the stator 40 and the rotor 30 drops downward and accumulates in the lower area inside the motor housing 81 .
  • the oil O accumulated in the lower region inside the motor housing 81 returns into the gear housing 82 through the partition wall opening 81d provided in the partition wall portion 81b.
  • coolant flow path 90 supplies oil O stored in gear housing 82 to rotor 30 and stator 40 .
  • the oil O can flow through the shaft 1. Then, when the rotor 30 rotates over a predetermined number of revolutions, the oil O is preferentially discharged from the coolant supply hole 33 by centrifugal force. At this time, in the shaft 1, the flow of the oil O along the direction of the central axis J is not ensured on the downstream side of the coolant supply hole 33, the cooling efficiency for the rotor 30 is lowered, and the lubricating oil for the bearing 35 is The amount of oil O supplied may decrease. Therefore, the rotating electric machine 10 is configured to be able to eliminate such problems. This configuration and operation will be described below.
  • the shaft 1 includes a shaft body 2 and a cylindrical body 5 inserted into the shaft body 2.
  • the shaft main body 2 is composed of a cylindrical member whose total length is longer than that of the cylindrical body 5.
  • the shaft body 2 has a first screw portion 21 and a first side hole 22.
  • the first threaded portion 21 is a female thread provided on the upstream side portion of the inner peripheral surface 231 of the shaft body 2 .
  • the first threaded portion 21 is provided from the opening on the upstream side of the shaft body 2 halfway in the central axis J direction.
  • the first side hole 22 is a through hole penetrating through the shaft body 2 in the radial direction. Further, the first side hole 22 opens to the first screw portion 21 inside the shaft body 2 . Also, a plurality of first side holes 22 are provided. Although the number of the first side holes 22 arranged is eight in this embodiment, it is not limited to this, and may be, for example, two to seven or nine or more. The eight first side holes 22 are arranged at equal angular intervals around the central axis J and at the same position in the central axis J direction.
  • the shaft body 2 has an outer diameter that varies along the direction of the central axis J, an upstream small-diameter portion 233 , a downstream small-diameter portion 234 , and a large diameter between the small-diameter portions 233 and 234 . and a diameter portion 235 .
  • a cylindrical body 5 is inserted into the upstream side of the shaft body 2 .
  • the cylindrical body 5 has a second screw portion 51 and a second side hole 52.
  • the second screw portion 51 is a male screw provided on the outer peripheral surface 501 .
  • the second side hole 52 is a through hole penetrating through the cylindrical body 5 in the radial direction. Also, the second side hole 52 opens to the second screw portion 51 on the outside of the cylindrical body 5 .
  • a plurality of second side holes 52 are provided. In the present embodiment, the number of the second side holes 52 arranged is eight, which is the same number as the number of the first side holes 22 arranged.
  • the eight second side holes 52 are arranged at equal angular intervals around the central axis J and at the same position in the central axis J direction.
  • the cylindrical body 5 has, on the outer peripheral surface 501, a flange portion 53 that protrudes radially outward, that is, has an enlarged outer diameter.
  • the flange portion 53 is located at the upstream end of the cylindrical body 5 .
  • the second threaded portion 51 By rotating the cylindrical body 5 (second threaded portion 51) configured as described above about the central axis J with respect to the shaft body 2, the second threaded portion 51 is rotated as shown in FIGS. 1 threaded portion 21 to fit the threaded portions together.
  • the cylindrical body 5 can be attached to the upstream side of the shaft body 2 (one side in the central axis J direction).
  • the screwing amount (rotation amount) of the second threaded portion 51 with respect to the first threaded portion 21 is appropriately adjusted according to various conditions such as the type of the rotary electric machine 10 on which the shaft 1 is mounted, for example (see FIG. 5, see Figure 6). Further, the adjustment of the amount of screwing facilitates the positioning of the cylindrical body 5 with respect to the shaft body 2 .
  • the cylindrical body 5 creates a gap GP between the flange portion 53 and the end surface 202 of the shaft body 2 until the flange portion 53 comes into contact with the end surface 202 of the shaft body 2 . It is screwed into the shaft body 2 to an extent.
  • the separation distance SD between the second side hole 52 and the first side hole 22 in the direction of the central axis J can be set larger than the separation distance SD in the attached state shown in FIG.
  • the plurality of second side holes 52 are located upstream of the plurality of first side holes 22 regardless of the amount of screwing.
  • the plurality of first side holes 22 and the plurality of second side holes 52 are connected via the first threaded portion 21 and the second threaded portion 51 .
  • the flow path 12 is the coolant supply hole 33 .
  • the oil O flowing into the shaft 1 from the opening 201 includes the oil O1 that flows directly downstream beyond the second side hole 52 and the oil O1 that flows toward the flow path 12 via the second side hole 52. O2 is present. In this state, when the rotor 30 rotates over a predetermined number of revolutions, the oil O is likely to be preferentially discharged from the second side holes 52 due to centrifugal force.
  • the second side holes 52 and the first side holes 22 are displaced in the direction of the central axis J, the flow of the oil O2 toward the flow path 12 is suppressed. Since the flow of the oil O2 is suppressed, the flow of the oil O1 can be sufficiently secured. As a result, regardless of the rotational speed of the rotor 30, the cooling efficiency of the stator 40 can be improved by the oil O2, and the cooling efficiency of the rotor 30 can be sufficiently improved by the oil O1. Also, the oil O1 can sufficiently function as a lubricating oil for the bearings 35 .
  • the rotation direction of the shaft 1 and the screw directions of the first threaded portion 21 and the second threaded portion 51 are the same.
  • the screw directions of the first threaded portion 21 and the second threaded portion 51 are right-handed. This allows the oil O2 to smoothly pass from the second side hole 52 to the first side hole 22 .
  • the outer diameter ⁇ D51 of the second screw 51 male screw
  • the outer diameter ⁇ D51 of the second screw 51 is preferably 80% or more and 95% or less of the root diameter ⁇ D21 of the first screw 21 (female screw). More preferably, it is 90% or less.
  • the space between the first threaded portion 21 and the second threaded portion 51 is widened as much as possible while the fitting state between the first threaded portion 21 and the second threaded portion 51 is sufficiently maintained, thereby facilitating the flow of the oil O2. can be passed to
  • the thread ridge 511 of the second screw 51 (male screw) and the screw groove 211 of the first screw 21 (female screw) have at least one size or shape in side view when viewed from the radial direction. different.
  • both the shape of the thread 511 and the shape of the thread groove 211 are triangular, but the thread 511 is smaller than the thread groove 211 .
  • This also widens the space between the first threaded portion 21 and the second threaded portion 51 as much as possible, contributing to easy passage of the oil O2.
  • the flow rate of the oil O2 can be adjusted by appropriately changing the design of at least one of the size and shape of each screw.
  • the separation distance SD between the first side hole 22 and the second side hole 52 can be adjusted by changing the amount of screwing of the second threaded portion 51 into the first threaded portion 21 .
  • the smaller the separation distance SD the more the flow rate of the oil O from the second side hole 52 to the first side hole 22 can be increased.
  • the larger the clearance SD is, the more the flow rate of the oil O2 from the second side hole 52 to the first side hole 22 can be reduced. Therefore, the flow rate of the oil O2 can also be adjusted depending on the distance SD.
  • the materials for the shaft body 2 and the cylindrical body 5 are not particularly limited, and for example, hard materials such as metal materials and resin materials can be used.
  • the rotating electric machine and the drive device of the present invention have been described with reference to the illustrated embodiments, but the present invention is not limited to this, and each part constituting the rotating electric machine and the drive device performs the same function. can be substituted with any configuration available. Moreover, arbitrary components may be added. Also, a plurality of types of cylindrical bodies 5 having different arrangement positions and numbers of the second side holes 52 in the direction of the central axis J may be prepared in advance. In this case, an appropriate cylindrical body 5 can be selected from a plurality of types of cylindrical bodies 5 and attached to the shaft main body 2 according to various conditions such as the type of the rotating electric machine 10 on which the shaft 1 is mounted. . Further, the cylindrical body 5 is composed of one continuous member, but is not limited to this, and for example, has a configuration including a divided body divided into at least two along the direction of the central axis J. may

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Power Engineering (AREA)
  • Motor Or Generator Cooling System (AREA)

Abstract

Provided are a rotating electric machine in which the efficiency of cooling a rotor and a stator is improved and a drive device. This rotating electric machine 10 comprises a rotor 30 having a shaft 1 and a stator located outside the rotor 30 in the radial direction. The shaft 1 comprises: a cylindrical shaft body 2 having a first screw portion 21 provided on the inner circumferential surface 231 and a plurality of first side holes 22 penetrating in the radial direction; and a cylindrical body 5 having a second screw portion 51 provided on the outer circumferential surface 501 and a plurality of second side holes 52 penetrating in the radial direction. The second screw portion 51 is rotated and fitted into the first screw portion 21, and thereby, in an attachment state in which the cylindrical body 5 is attached to one side of the shaft body 2 in the axis J direction, the plurality of second side holes 52 are located on the one side in the axis J direction with respect to the plurality of first side holes 22. The plurality of first side holes 22 and the plurality of second side holes 52 are connected to each other through between the first screw portion 21 and the second screw portion 51 and function as flow paths 12 through which an oil O can pass.

Description

回転電機および駆動装置Rotating electric machine and drive
　本発明は、回転電機および駆動装置に関する。 The present invention relates to a rotating electric machine and a driving device.
　回転軸を有する回転子と、回転子が内側に配置され、回転磁場により回転子を回転駆動させる固定子とを備える電動機が知られている（例えば、特許文献１参照）。　特許文献１に記載の電動機の回転子は、回転軸が中空に構成される。そして、回転軸内に冷却オイル等の冷媒を流通させることにより、回転子の温度上昇を抑制することができる。 An electric motor is known that includes a rotor having a rotating shaft and a stator in which the rotor is arranged and that rotates the rotor by a rotating magnetic field (see, for example, Patent Document 1). The rotor of the electric motor described in Patent Document 1 has a hollow rotating shaft. By circulating a coolant such as cooling oil in the rotating shaft, it is possible to suppress the temperature rise of the rotor.
特開２００３－２３５２１０号公報JP-A-2003-235210
　しかしながら、特許文献１に記載の電動機では、冷媒が回転軸内を通過するため、回転子の温度上昇を抑制することができるが、固定子の温度上昇までも抑制するのが困難である。すなわち、特許文献１に記載の電動機では、回転子および固定子の双方に対する冷却効率が低い。　本発明の目的は、ロータおよびステータに対する冷却効率が向上する回転電機および駆動装置を提供することにある。 However, in the electric motor described in Patent Document 1, since the coolant passes through the rotating shaft, it is possible to suppress the temperature rise of the rotor, but it is difficult to suppress even the temperature rise of the stator. That is, in the electric motor disclosed in Patent Document 1, cooling efficiency for both the rotor and the stator is low. An object of the present invention is to provide a rotating electric machine and a driving device that improve cooling efficiency for the rotor and stator.
　本発明の回転電機の一つの態様は、内部に冷媒が流通可能なシャフトを有し、該シャフトを回転中心として回転可能なロータと、
　該ロータの径方向外側に位置するステータとを備え、
　前記シャフトは、
　内周面に設けられた第１ネジ部と、径方向に貫通する複数の第１側孔とを有する円筒状のシャフト本体と、
　外周面に設けられた第２ネジ部と、径方向に貫通する複数の第２側孔とを有する円筒体とを備え、
　前記第２ネジ部を回転により前記第１ネジ部に嵌め合わせることにより、前記円筒体を前記シャフト本体の軸方向一方側に取り付けた取付状態で、前記複数の第２側孔が前記複数の第１側孔より軸方向一方側に位置し、
　前記複数の第１側孔と前記複数の第２側孔とが、前記第１ネジ部と前記第２ネジ部との間を介して繋がり、前記冷媒が通過可能な流路として機能することを特徴とする。 In one aspect of the rotating electric machine of the present invention, a rotor having a shaft in which a coolant can flow and rotatable around the shaft;
a stator positioned radially outward of the rotor,
The shaft is
a cylindrical shaft body having a first threaded portion provided on an inner peripheral surface and a plurality of first side holes penetrating in a radial direction;
A cylindrical body having a second threaded portion provided on the outer peripheral surface and a plurality of second side holes penetrating in the radial direction,
By rotating the second threaded portion to fit the first threaded portion, the plurality of second side holes are aligned with the plurality of second side holes in a mounting state in which the cylindrical body is mounted on one side of the shaft body in the axial direction. Located on one side in the axial direction from the 1 side hole,
The plurality of first side holes and the plurality of second side holes are connected via between the first screw portion and the second screw portion, and function as a flow path through which the refrigerant can pass. Characterized by
　本発明の駆動装置の一つの態様は、車両に搭載され、車軸を回転させる駆動装置であって、
　上記に記載の回転電機と、
　前記回転電機に接続され、前記ロータの回転を前記車軸に伝達する伝達装置と、
　前記回転電機および前記伝達装置を収容するハウジングと、
　前記ハウジング内に設けられ、前記回転電機の前記シャフト内および前記ステータに冷媒を供給する冷媒流路とを備えることを特徴とする。 One aspect of the drive device of the present invention is a drive device that is mounted on a vehicle and rotates an axle,
The rotating electrical machine described above;
a transmission device that is connected to the rotating electrical machine and that transmits rotation of the rotor to the axle;
a housing that accommodates the rotating electric machine and the transmission device;
and a coolant passage provided in the housing for supplying a coolant to the shaft and the stator of the rotating electric machine.
　本発明によれば、ロータおよびステータに対する冷却効率が向上する。 According to the present invention, cooling efficiency for the rotor and stator is improved.
図１は、一実施形態の駆動装置を模式的に示す概略構成図である。FIG. 1 is a schematic configuration diagram schematically showing a driving device according to one embodiment. 図２は、ロータが有するシャフトの縦断面図である。FIG. 2 is a longitudinal sectional view of a shaft that the rotor has. 図３は、ロータが有するシャフトの拡大縦断面図である。FIG. 3 is an enlarged vertical cross-sectional view of a shaft that the rotor has. 図４は、図３中の一点鎖線で囲まれた領域［Ａ］の拡大図である。FIG. 4 is an enlarged view of a region [A] surrounded by a dashed line in FIG. 図５は、ロータにおけるシャフト本体と円筒体との位置関係を示す縦断面図である。FIG. 5 is a longitudinal sectional view showing the positional relationship between the shaft body and the cylindrical body in the rotor. 図６は、ロータにおけるシャフト本体と円筒体との位置関係を示す縦断面図である。FIG. 6 is a longitudinal sectional view showing the positional relationship between the shaft body and the cylindrical body in the rotor. 図７は、シャフト本体の縦断面斜視図である。FIG. 7 is a vertical cross-sectional perspective view of the shaft body. 図８は、円筒体の縦断面斜視図である。FIG. 8 is a vertical cross-sectional perspective view of a cylindrical body.
　以下、図１～図８を参照して、本発明の回転電機および駆動装置を添付図面に示す好適な実施形態に基づいて詳細に説明する。  以下の説明では、本実施形態の駆動装置が水平な路面上に位置する車両に搭載された場合を一例としている。　また、適宜図に示す中心軸Ｊは、鉛直方向と交差する方向に延びる仮想軸である。以下の説明では、中心軸Ｊに平行な方向を単に「軸方向」と、中心軸Ｊを中心とする径方向を単に「径方向」と、中心軸Ｊを中心とする周方向（中心軸Ｊの軸回り）を単に「周方向」と呼ぶ場合がある。 1 to 8, a rotating electric machine and a driving device of the present invention will be described in detail based on preferred embodiments shown in the accompanying drawings. In the following description, a case where the driving device of this embodiment is mounted on a vehicle positioned on a horizontal road surface is taken as an example. Also, the central axis J shown in the drawing as appropriate is a virtual axis extending in a direction intersecting the vertical direction. In the following description, the direction parallel to the central axis J is simply referred to as the "axial direction," the radial direction about the central axis J is simply referred to as the "radial direction," and the circumferential direction about the central axis J (the central axis J axis) is sometimes simply referred to as the "circumferential direction".
　また、本明細書中において、上下方向、水平方向、上側および下側とは、単に各部の相対位置関係を説明するための名称であり、実際の配置関係等は、これらの名称で示される配置関係等以外の配置関係等であってもよい。　なお、図２～図８中、左側を「上流側」、右側を「下流側」と言う。また、図示の構成では、「上流側」が「軸（中心軸Ｊ）方向一方側」に、「下流側」が「軸（中心軸Ｊ）方向他方側」に相当する。 Further, in this specification, the vertical direction, the horizontal direction, the upper side, and the lower side are names for simply explaining the relative positional relationship of each part, and the actual positional relationship, etc. are the positions indicated by these names. A layout relationship other than the relationship may be used. In addition, in FIGS. 2 to 8, the left side is called "upstream side" and the right side is called "downstream side". Further, in the illustrated configuration, the “upstream side” corresponds to “one side in the axial (central axis J) direction”, and the “downstream side” corresponds to “the other side in the axial (central axis J) direction”.
　図１に示す本実施形態の駆動装置１００は、車両に搭載され、車軸６４を回転させる駆動装置である。駆動装置１００が搭載される車両は、ハイブリッド自動車（ＨＥＶ）、プラグインハイブリッド自動車（ＰＨＶ）、電気自動車（ＥＶ）等のモータを動力源とする車両である。図１に示すように、駆動装置１００は、回転電機１０と、ハウジング８０と、伝達装置６０と、冷媒流路９０とを備える。回転電機１０は、中心軸（軸）Ｊを中心として回転可能なロータ３０と、ロータ３０の径方向外側に位置するステータ４０とを備える。 A driving device 100 of the present embodiment shown in FIG. 1 is mounted on a vehicle and rotates an axle 64 . A vehicle in which drive device 100 is mounted is a vehicle using a motor as a power source, such as a hybrid vehicle (HEV), a plug-in hybrid vehicle (PHV), an electric vehicle (EV), or the like. As shown in FIG. 1 , drive device 100 includes rotary electric machine 10 , housing 80 , transmission device 60 , and coolant channel 90 . The rotary electric machine 10 includes a rotor 30 rotatable around a central axis (axis) J and a stator 40 located radially outside the rotor 30 .
　ハウジング８０は、回転電機１０および伝達装置６０を収容する。ハウジング８０は、モータハウジング８１と、ギヤハウジング８２と、を有する。モータハウジング８１は、ロータ３０およびステータ４０を内部に収容するハウジングである。モータハウジング８１は、ギヤハウジング８２の右側に繋がっている。モータハウジング８１は、周壁部８１ａと、隔壁部８１ｂと、蓋部８１ｃとを有する。周壁部８１ａと隔壁部８１ｂとは、例えば、同一の単一部材の一部である。蓋部８１ｃは、例えば、周壁部８１ａおよび隔壁部８１ｂとは別体である。 The housing 80 accommodates the rotary electric machine 10 and the transmission device 60 . Housing 80 has a motor housing 81 and a gear housing 82 . Motor housing 81 is a housing that accommodates rotor 30 and stator 40 therein. The motor housing 81 is connected to the right side of the gear housing 82 . The motor housing 81 has a peripheral wall portion 81a, a partition wall portion 81b, and a lid portion 81c. The peripheral wall portion 81a and the partition wall portion 81b are, for example, part of the same single member. The lid portion 81c is separate from, for example, the peripheral wall portion 81a and the partition wall portion 81b.
　周壁部８１ａは、中心軸Ｊを囲み、右側に開口する筒状である。隔壁部８１ｂは、周壁部８１ａの左側の端部に繋がっている。隔壁部８１ｂは、モータハウジング８１の内部とギヤハウジング８２の内部とを軸方向に隔てている。隔壁部８１ｂは、モータハウジング８１の内部とギヤハウジング８２の内部とを繋ぐ隔壁開口８１ｄを有する。隔壁部８１ｂには、ベアリング３４が保持されている。蓋部８１ｃは、周壁部８１ａの右側の端部に固定されている。蓋部８１ｃは、周壁部８１ａの右側の開口を塞いでいる。蓋部８１ｃには、ベアリング３５が保持されている。 The peripheral wall portion 81a has a tubular shape surrounding the central axis J and opening on the right side. The partition wall portion 81b is connected to the left end portion of the peripheral wall portion 81a. The partition wall portion 81b separates the interior of the motor housing 81 and the interior of the gear housing 82 in the axial direction. The partition wall portion 81 b has a partition wall opening 81 d that connects the inside of the motor housing 81 and the inside of the gear housing 82 . A bearing 34 is held in the partition portion 81b. The lid portion 81c is fixed to the right end of the peripheral wall portion 81a. The lid portion 81c closes the opening on the right side of the peripheral wall portion 81a. A bearing 35 is held in the lid portion 81c.
　ギヤハウジング８２は、伝達装置６０の減速装置６２および差動装置６３と、オイルＯとを内部に収容している。オイルＯは、ギヤハウジング８２内の下部領域に貯留されている。オイルＯは、冷媒流路９０内を循環する。オイルＯは、回転電機１０を冷却する冷媒として使用される。また、オイルＯは、減速装置６２および差動装置６３に対して潤滑油として使用される。オイルＯとしては、例えば、冷媒および潤滑油の機能を奏するために、比較的粘度の低いオートマチックトランスミッション用潤滑油（ＡＴＦ：Automatic Transmission Fluid）と同等のオイルを用いることが好ましい。 The gear housing 82 accommodates the reduction gear 62 and the differential gear 63 of the transmission device 60 and the oil O inside. The oil O is stored in the lower area inside the gear housing 82 . The oil O circulates inside the coolant flow path 90 . Oil O is used as a coolant for cooling rotating electric machine 10 . Also, the oil O is used as a lubricating oil for the reduction gear 62 and the differential gear 63 . As the oil O, for example, it is preferable to use an oil equivalent to automatic transmission fluid (ATF), which has a relatively low viscosity, in order to function as a refrigerant and a lubricating oil.
　伝達装置６０は、回転電機１０に接続され、ロータ３０の回転を車両の車軸６４に伝達する。本実施形態の伝達装置６０は、回転電機１０に接続される減速装置６２と、減速装置６２に接続される差動装置６３とを有する。　差動装置６３は、リングギヤ６３ａを有する。リングギヤ６３ａには、回転電機１０から出力されるトルクが減速装置６２を介して伝えられる。リングギヤ６３ａの下側の端部は、ギヤハウジング８２内に貯留されたオイルＯに浸漬している。リングギヤ６３ａが回転することで、オイルＯがかき上げられる。かき上げられたオイルＯは、例えば、減速装置６２および差動装置６３に潤滑油として供給される。 The transmission device 60 is connected to the rotating electric machine 10 and transmits the rotation of the rotor 30 to the axle 64 of the vehicle. A transmission device 60 of the present embodiment has a reduction gear 62 connected to the rotating electric machine 10 and a differential gear 63 connected to the reduction gear 62 . The differential gear 63 has a ring gear 63a. Torque output from the rotary electric machine 10 is transmitted to the ring gear 63 a via the reduction gear 62 . A lower end portion of the ring gear 63 a is immersed in the oil O stored in the gear housing 82 . The oil O is scooped up by the rotation of the ring gear 63a. The scooped-up oil O is supplied as lubricating oil to, for example, the reduction gear 62 and the differential gear 63 .
　回転電機１０は、駆動装置１００を駆動する部分である。回転電機１０は、例えば、伝達装置６０の右側に位置する。本実施形態において回転電機１０は、モータである。回転電機１０のロータ３０のトルクは、伝達装置６０に伝達される。ロータ３０は、中心軸Ｊを中心として軸方向に延びるシャフト１と、シャフト１に固定されるロータ本体３２と、を有する。ロータ本体３２は、例えば、シャフト１の外周面に固定され軸方向に並ぶ複数のロータコア部と、各ロータコア部にそれぞれ保持されるマグネット等で構成される。 The rotating electrical machine 10 is a part that drives the driving device 100 . The rotating electrical machine 10 is positioned, for example, on the right side of the transmission device 60 . In this embodiment, the rotating electric machine 10 is a motor. Torque of rotor 30 of rotating electric machine 10 is transmitted to transmission device 60 . The rotor 30 has a shaft 1 extending axially around a central axis J and a rotor body 32 fixed to the shaft 1 . The rotor main body 32 is composed of, for example, a plurality of rotor core portions fixed to the outer peripheral surface of the shaft 1 and arranged in the axial direction, and magnets and the like held in each rotor core portion.
　図１に示すように、シャフト１は、中心軸Ｊを中心として回転可能である。これにより、ロータ３０は、シャフト１を回転中心として回転することができる。シャフト１は、ベアリング３４、ベアリング３５によって回転可能に支持されている。本実施形態においてシャフト１は、中空シャフトである。シャフト１は、内部に冷媒としてのオイルＯが流通可能な筒状である。シャフト１は、モータハウジング８１の内部とギヤハウジング８２の内部とに跨って延びている。シャフト１の左側の端部は、ギヤハウジング８２の内部に突出している。シャフト１の左側の端部には、減速装置６２が接続されている。 As shown in FIG. 1, the shaft 1 is rotatable around the central axis J. Thereby, the rotor 30 can rotate around the shaft 1 . The shaft 1 is rotatably supported by bearings 34 and 35 . In this embodiment the shaft 1 is a hollow shaft. The shaft 1 has a cylindrical shape through which oil O as a coolant can flow. The shaft 1 extends across the interior of the motor housing 81 and the interior of the gear housing 82 . The left end of the shaft 1 protrudes inside the gear housing 82 . A reduction gear 62 is connected to the left end of the shaft 1 .
　ステータ４０は、ロータ３０と径方向外側に隙間を介して位置する。ステータ４０は、ロータ３０を径方向外側から周方向全周にわたって囲う。ステータ４０は、モータハウジング８１の内部に固定される。ステータ４０は、ステータコア４１と、コイルアセンブリ４２とを有する。 The stator 40 is positioned radially outwardly of the rotor 30 with a gap therebetween. The stator 40 surrounds the rotor 30 from the radially outer side along the entire circumference. The stator 40 is fixed inside the motor housing 81 . Stator 40 has a stator core 41 and a coil assembly 42 .
　ステータコア４１は、回転電機１０の中心軸Ｊを囲む環状である。ステータコア４１は、例えば、電磁鋼板などの板部材が軸方向に複数積層されて構成されている。コイルアンブリ４２は、周方向に沿ってステータコア４１に取り付けられる複数のコイル４２ｃを有する。複数のコイル４２ｃは、インシュレータ（図示省略）を介してステータコア４１の各ティース（図示省略）にそれぞれ装着されている。複数のコイル４２ｃは、周方向に沿って配置されている。コイル４２ｃは、ステータコア４１から軸方向に突出する部分を有する。 The stator core 41 has an annular shape surrounding the central axis J of the rotary electric machine 10 . The stator core 41 is configured, for example, by laminating a plurality of plate members such as electromagnetic steel plates in the axial direction. The coil assembly 42 has a plurality of coils 42c attached to the stator core 41 along the circumferential direction. The plurality of coils 42c are attached to respective teeth (not shown) of the stator core 41 via insulators (not shown). A plurality of coils 42c are arranged along the circumferential direction. Coil 42c has a portion protruding from stator core 41 in the axial direction.
　冷媒流路９０は、ハウジング８０内に設けられる。冷媒流路９０には、冷媒としてのオイルＯが流れる。冷媒流路９０は、モータハウジング８１の内部とギヤハウジング８２の内部とに跨って設けられている。冷媒流路９０は、ギヤハウジング８２内に貯留されたオイルＯがモータハウジング８１内の回転電機１０に供給されて再びギヤハウジング８２内に戻る経路である。冷媒流路９０には、ポンプ７１と、クーラ７２とが設けられている。冷媒流路９０は、第１流路部９１と、第２流路部９２と、第３流路部９３と、ステータ冷媒供給部５０と、シャフト流路部９５と、接続流路部９４と、径方向流路部９６と、軸方向流路部９８と、ガイド流路部９７とを有する。 The coolant channel 90 is provided inside the housing 80 . Oil O as a coolant flows through the coolant channel 90 . The coolant flow path 90 is provided across the inside of the motor housing 81 and the inside of the gear housing 82 . The coolant flow path 90 is a path through which the oil O stored in the gear housing 82 is supplied to the rotating electric machine 10 in the motor housing 81 and returns to the gear housing 82 again. A pump 71 and a cooler 72 are provided in the coolant channel 90 . The coolant channel 90 includes a first channel portion 91 , a second channel portion 92 , a third channel portion 93 , a stator coolant supply portion 50 , a shaft channel portion 95 , and a connection channel portion 94 . , a radial channel portion 96 , an axial channel portion 98 , and a guide channel portion 97 .
　第１流路部９１、第２流路部９２、および第３流路部９３は、例えば、ギヤハウジング８２の壁部に設けられている。第１流路部９１は、ギヤハウジング８２の内部のうちオイルＯが貯留されている部分とポンプ７１とを繋いでいる。第２流路部９２は、ポンプ７１とクーラ７２とを繋いでいる。第３流路部９３は、クーラ７２とステータ冷媒供給部５０とを繋いでいる。本実施形態において第３流路部９３は、ステータ冷媒供給部５０の左側の端部すなわちステータ冷媒供給部５０の上流側部分に繋がっている。 The first flow path part 91, the second flow path part 92, and the third flow path part 93 are provided on the wall of the gear housing 82, for example. The first flow path portion 91 connects a portion of the gear housing 82 where the oil O is stored and the pump 71 . The second channel portion 92 connects the pump 71 and the cooler 72 . The third flow path portion 93 connects the cooler 72 and the stator coolant supply portion 50 . In the present embodiment, the third flow path portion 93 is connected to the left end portion of the stator coolant supply portion 50 , that is, the upstream portion of the stator coolant supply portion 50 .
　ステータ冷媒供給部５０は、ステータ４０にオイルＯを供給する。本実施形態においてステータ冷媒供給部５０は、軸方向に延びる管状である。言い換えれば、本実施形態においてステータ冷媒供給部５０は、軸方向に延びるパイプである。ステータ冷媒供給部５０の軸方向両端部は、モータハウジング８１に支持されている。ステータ冷媒供給部５０の左側の端部は、例えば、隔壁部８１ｂに支持されている。ステータ冷媒供給部５０の右側の端部は、例えば、蓋部８１ｃに支持されている。ステータ冷媒供給部５０は、ステータ４０の径方向外側に位置する。本実施形態においてステータ冷媒供給部５０は、ステータ４０の上側に位置する。 A stator coolant supply unit 50 supplies oil O to the stator 40 . In this embodiment, the stator coolant supply portion 50 has a tubular shape extending in the axial direction. In other words, in this embodiment, the stator coolant supply portion 50 is a pipe extending in the axial direction. Both axial end portions of the stator coolant supply portion 50 are supported by the motor housing 81 . A left end portion of the stator coolant supply portion 50 is supported by, for example, the partition portion 81b. A right end portion of the stator coolant supply portion 50 is supported by, for example, the lid portion 81c. The stator coolant supply portion 50 is positioned radially outward of the stator 40 . In this embodiment, the stator coolant supply section 50 is positioned above the stator 40 .
　ステータ冷媒供給部５０は、ステータ４０にオイルＯを供給する供給口５０ａを有する。本実施形態において供給口５０ａは、ステータ冷媒供給部５０内に流入したオイルＯの一部をステータ冷媒供給部５０の外部に噴射させる噴射口である。供給口５０ａは、ステータ冷媒供給部５０の壁部を内周面から外周面まで貫通する孔によって構成されている。供給口５０ａは、ステータ冷媒供給部５０に複数設けられている。複数の供給口５０ａは、例えば、軸方向または周方向に互いに間隔をあけて配置される。 The stator coolant supply section 50 has a supply port 50a for supplying the oil O to the stator 40 . In the present embodiment, the supply port 50 a is an injection port that injects part of the oil O that has flowed into the stator coolant supply portion 50 to the outside of the stator coolant supply portion 50 . The supply port 50a is formed by a hole penetrating the wall portion of the stator coolant supply portion 50 from the inner peripheral surface to the outer peripheral surface. A plurality of supply ports 50 a are provided in the stator coolant supply portion 50 . The plurality of supply ports 50a are spaced apart from each other, for example, in the axial direction or the circumferential direction.
　シャフト流路部９５は、シャフト１内に配置される。これにより、シャフト１内にオイルＯを供給することができる。　また、接続流路部９４は、ステータ冷媒供給部５０の内部とシャフト１の内部とを繋いでいる。接続流路部９４は、ステータ冷媒供給部５０の右側の端部つまり下流側部分と、シャフト流路部９５の右側の端部つまり上流側部分と、を接続する。接続流路部９４は、例えば、蓋部８１ｃに設けられている。本実施形態によれば、冷媒流路９０の構成を簡素化しつつ、ステータ４０およびロータ３０を安定して冷却できる。　軸方向流路部９８は、径方向流路部９６とガイド流路部９７とを繋ぐ。軸方向流路部９８は、複数のロータコア部の内部にわたって配置される。 The shaft channel portion 95 is arranged inside the shaft 1 . Thereby, the oil O can be supplied into the shaft 1 . In addition, the connection channel portion 94 connects the inside of the stator coolant supply portion 50 and the inside of the shaft 1 . The connection channel portion 94 connects the right end portion of the stator coolant supply portion 50 , that is, the downstream portion, and the right end portion of the shaft channel portion 95 , that is, the upstream portion. The connection channel portion 94 is provided, for example, in the lid portion 81c. According to this embodiment, it is possible to stably cool the stator 40 and the rotor 30 while simplifying the configuration of the coolant flow path 90 . The axial channel portion 98 connects the radial channel portion 96 and the guide channel portion 97 . The axial channel portion 98 is arranged over the interior of the plurality of rotor core portions.
　図１に示すように、ポンプ７１が駆動されると、ギヤハウジング８２内に貯留されたオイルＯが第１流路部９１を通って吸い上げられ、第２流路部９２を通ってクーラ７２内に流入する。クーラ７２内に流入したオイルＯは、クーラ７２内で冷却された後、第３流路部９３を通って、ステータ冷媒供給部５０へと流れる。ステータ冷媒供給部５０内に流入したオイルＯの一部は、供給口５０ａから噴射されて、ステータ４０に供給される。ステータ冷媒供給部５０内に流入したオイルＯの他の一部は、接続流路部９４を通ってシャフト流路部９５に流入する。シャフト流路部９５を流れるオイルＯの一部は、冷媒供給孔３３から径方向流路部９６、軸方向流路部９８およびガイド流路部９７を流れて、ステータ４０に飛散する。シャフト流路部９５に流入したオイルＯの他の一部は、シャフト１の左側の開口からギヤハウジング８２の内部に排出され、再びギヤハウジング８２内に貯留される。 As shown in FIG. 1, when the pump 71 is driven, the oil O stored in the gear housing 82 is sucked up through the first flow passage portion 91 and then through the second flow passage portion 92 into the cooler 72. flow into The oil O that has flowed into the cooler 72 is cooled in the cooler 72 and then flows through the third flow path portion 93 to the stator coolant supply portion 50 . A portion of the oil O that has flowed into the stator coolant supply portion 50 is injected from the supply port 50 a and supplied to the stator 40 . Another part of the oil O that has flowed into the stator coolant supply portion 50 flows into the shaft flow channel portion 95 through the connection flow channel portion 94 . A portion of the oil O flowing through the shaft channel portion 95 flows from the coolant supply hole 33 through the radial channel portion 96 , the axial channel portion 98 , and the guide channel portion 97 and scatters to the stator 40 . Another part of the oil O that has flowed into the shaft flow path portion 95 is discharged into the gear housing 82 through the left opening of the shaft 1 and is stored in the gear housing 82 again.
　供給口５０ａからステータ４０に供給されたオイルＯは、ステータ４０から熱を奪い、シャフト１内からロータ３０およびステータ４０に供給されたオイルＯは、ロータ３０およびステータ４０から熱を奪う。ステータ４０およびロータ３０を冷却したオイルＯは、下側に落下して、モータハウジング８１内の下部領域に溜まる。モータハウジング８１内の下部領域に溜ったオイルＯは、隔壁部８１ｂに設けられた隔壁開口８１ｄを介してギヤハウジング８２内に戻る。以上のようにして、冷媒流路９０は、ギヤハウジング８２内に貯留されたオイルＯをロータ３０およびステータ４０に供給する。 The oil O supplied to the stator 40 from the supply port 50 a takes heat from the stator 40 , and the oil O supplied to the rotor 30 and stator 40 from within the shaft 1 takes heat from the rotor 30 and stator 40 . The oil O that has cooled the stator 40 and the rotor 30 drops downward and accumulates in the lower area inside the motor housing 81 . The oil O accumulated in the lower region inside the motor housing 81 returns into the gear housing 82 through the partition wall opening 81d provided in the partition wall portion 81b. As described above, coolant flow path 90 supplies oil O stored in gear housing 82 to rotor 30 and stator 40 .
　前述したように、オイルＯは、シャフト１内を流通することができる。そして、ロータ３０が所定の回転数を超えて回転した場合、オイルＯは、遠心力によって優先的に冷媒供給孔３３から排出されることとなる。このとき、シャフト１内では、冷媒供給孔３３より下流側において中心軸Ｊ方向に沿ったオイルＯの流れが確保されず、ロータ３０に対する冷却効率が低下したり、ベアリング３５への潤滑油としてのオイルＯの供給量が減少するおそれがある。　そこで、回転電機１０では、このような不具合を解消可能に構成される。以下、この構成および作用について説明する。 As described above, the oil O can flow through the shaft 1. Then, when the rotor 30 rotates over a predetermined number of revolutions, the oil O is preferentially discharged from the coolant supply hole 33 by centrifugal force. At this time, in the shaft 1, the flow of the oil O along the direction of the central axis J is not ensured on the downstream side of the coolant supply hole 33, the cooling efficiency for the rotor 30 is lowered, and the lubricating oil for the bearing 35 is The amount of oil O supplied may decrease. Therefore, the rotating electric machine 10 is configured to be able to eliminate such problems. This configuration and operation will be described below.
　図２、図３に示すように、シャフト１は、シャフト本体２と、シャフト本体２に挿入される円筒体５とを備える。　シャフト本体２は、全長が円筒体５よりも長い円筒状の部材で構成される。　図７に示すように、シャフト本体２は、第１ネジ部２１と、第１側孔２２とを有する。　第１ネジ部２１は、シャフト本体２の内周面２３１の上流側の部分に設けられた雌ネジである。本実施形態では、第１ネジ部２１は、シャフト本体２の上流側の開口部から、中心軸Ｊ方向の途中まで設けられる。 As shown in FIGS. 2 and 3, the shaft 1 includes a shaft body 2 and a cylindrical body 5 inserted into the shaft body 2. The shaft main body 2 is composed of a cylindrical member whose total length is longer than that of the cylindrical body 5. As shown in FIG. 7, the shaft body 2 has a first screw portion 21 and a first side hole 22. The first threaded portion 21 is a female thread provided on the upstream side portion of the inner peripheral surface 231 of the shaft body 2 . In this embodiment, the first threaded portion 21 is provided from the opening on the upstream side of the shaft body 2 halfway in the central axis J direction.
　第１側孔２２は、シャフト本体２の径方向に貫通する貫通孔である。また、第１側孔２２は、シャフト本体２の内側では、第１ネジ部２１に開口する。　また、第１側孔２２は、複数設けられる。第１側孔２２の配置数は、本実施形態では８つであるが、これに限定されず、例えば、２つ～７つまたは９つ以上であってもよい。　８つの第１側孔２２は、中心軸Ｊ回りに等角度間隔に配置されるとともに、中心軸Ｊ方向では同じ位置に配置される。　また、シャフト本体２は、外径が中心軸Ｊ方向に沿って変化しており、上流側の小径部２３３と、下流側の小径部２３４と、小径部２３３と小径部２３４との間の大径部２３５とを有する。 The first side hole 22 is a through hole penetrating through the shaft body 2 in the radial direction. Further, the first side hole 22 opens to the first screw portion 21 inside the shaft body 2 . Also, a plurality of first side holes 22 are provided. Although the number of the first side holes 22 arranged is eight in this embodiment, it is not limited to this, and may be, for example, two to seven or nine or more. The eight first side holes 22 are arranged at equal angular intervals around the central axis J and at the same position in the central axis J direction. Further, the shaft body 2 has an outer diameter that varies along the direction of the central axis J, an upstream small-diameter portion 233 , a downstream small-diameter portion 234 , and a large diameter between the small- diameter portions 233 and 234 . and a diameter portion 235 .
　シャフト本体２の上流側には、円筒体５が挿入される。　図８に示すように、円筒体５は、第２ネジ部５１と、第２側孔５２とを有する。　第２ネジ部５１は、外周面５０１に設けられた雄ネジである。　第２側孔５２は、円筒体５の径方向に貫通する貫通孔である。また、第２側孔５２は、円筒体５の外側では、第２ネジ部５１に開口する。　また、第２側孔５２は、複数設けられる。第２側孔５２の配置数は、本実施形態では第１側孔２２の配置数と同数の８つであるが、これに限定されず、例えば、２つ～７つまたは９つ以上であってもよい。　８つの第２側孔５２は、中心軸Ｊ回りに等角度間隔に配置されるとともに、中心軸Ｊ方向では同じ位置に配置される。　円筒体５は、径方向外側に向かって突出する、すなわち、外径が拡径したフランジ部５３を外周面５０１に有する。フランジ部５３は、円筒体５の上流側の端部に位置する。 A cylindrical body 5 is inserted into the upstream side of the shaft body 2 . As shown in FIG. 8, the cylindrical body 5 has a second screw portion 51 and a second side hole 52. The second screw portion 51 is a male screw provided on the outer peripheral surface 501 . The second side hole 52 is a through hole penetrating through the cylindrical body 5 in the radial direction. Also, the second side hole 52 opens to the second screw portion 51 on the outside of the cylindrical body 5 . Also, a plurality of second side holes 52 are provided. In the present embodiment, the number of the second side holes 52 arranged is eight, which is the same number as the number of the first side holes 22 arranged. may The eight second side holes 52 are arranged at equal angular intervals around the central axis J and at the same position in the central axis J direction. The cylindrical body 5 has, on the outer peripheral surface 501, a flange portion 53 that protrudes radially outward, that is, has an enlarged outer diameter. The flange portion 53 is located at the upstream end of the cylindrical body 5 .
　以上のような構成の円筒体５（第２ネジ部５１）をシャフト本体２に対して中心軸Ｊ回りに回転させることにより、図２、図３に示すように、第２ネジ部５１を第１ネジ部２１に捩じ込んで、ネジ部同士を嵌め合わせることができる。これにより、円筒体５をシャフト本体２の上流側（中心軸Ｊ方向一方側）に取り付けた取付状態とすることができる。　なお、第１ネジ部２１に対する第２ネジ部５１の捩じ込み量（回転量）は、例えばシャフト１が搭載される回転電機１０の種類等の諸条件に応じて、適宜調整される（図５、図６参照）。また、捩じ込み量の調整により、シャフト本体２に対する円筒体５の位置決めが容易となる。　図５（図２、図３についても同様）に示す取付状態では、円筒体５は、フランジ部５３がシャフト本体２の上流側の端面２０２に接触するまで、シャフト本体２に捩じ込まれている。これにより、第１ネジ部２１と第２ネジ部５１との捩じ込み限界（嵌め合わせ限界）を規制して、第１ネジ部２１と第２ネジ部５１との過剰な捩じ込みを防止することができる。 By rotating the cylindrical body 5 (second threaded portion 51) configured as described above about the central axis J with respect to the shaft body 2, the second threaded portion 51 is rotated as shown in FIGS. 1 threaded portion 21 to fit the threaded portions together. As a result, the cylindrical body 5 can be attached to the upstream side of the shaft body 2 (one side in the central axis J direction). The screwing amount (rotation amount) of the second threaded portion 51 with respect to the first threaded portion 21 is appropriately adjusted according to various conditions such as the type of the rotary electric machine 10 on which the shaft 1 is mounted, for example (see FIG. 5, see Figure 6). Further, the adjustment of the amount of screwing facilitates the positioning of the cylindrical body 5 with respect to the shaft body 2 . In the attached state shown in FIG. 5 (the same applies to FIGS. 2 and 3), the cylindrical body 5 is screwed into the shaft body 2 until the flange portion 53 contacts the upstream end face 202 of the shaft body 2 . there is As a result, the screwing limit (fitting limit) between the first threaded portion 21 and the second threaded portion 51 is regulated, and excessive screwing between the first threaded portion 21 and the second threaded portion 51 is prevented. can do.
　図６に示す取付状態では、円筒体５は、フランジ部５３がシャフト本体２の端面２０２に接触に至る前まで、すなわち、フランジ部５３がシャフト本体２の端面２０２と間に間隙ＧＰを生じさせる程度にシャフト本体２に捩じ込まれている。これにより、第２側孔５２と第１側孔２２との中心軸Ｊ方向における離間距離ＳＤを、図５に示す取付状態での離間距離ＳＤよりも大きく設定することができる。　また、図５、図６に示すように、取付状態では、捩じ込み量の大小に関わらず、複数の第２側孔５２が複数の第１側孔２２より上流側に位置する。 In the attached state shown in FIG. 6 , the cylindrical body 5 creates a gap GP between the flange portion 53 and the end surface 202 of the shaft body 2 until the flange portion 53 comes into contact with the end surface 202 of the shaft body 2 . It is screwed into the shaft body 2 to an extent. Thereby, the separation distance SD between the second side hole 52 and the first side hole 22 in the direction of the central axis J can be set larger than the separation distance SD in the attached state shown in FIG. Also, as shown in FIGS. 5 and 6, in the attached state, the plurality of second side holes 52 are located upstream of the plurality of first side holes 22 regardless of the amount of screwing.
　図３に示すように、複数の第１側孔２２と複数の第２側孔５２とは、第１ネジ部２１と第２ネジ部５１との間を介して繋がる。これにより、オイルＯが通過可能な流路１２が確保される。流路１２は、冷媒供給孔３３である。　また、シャフト１の開口部２０１から内部に流入したオイルＯには、第２側孔５２を超えて、そのまま下流側に向かうオイルＯ１と、第２側孔５２を介して流路１２に向かうオイルＯ２とが存在する。そして、この状態でロータ３０が所定の回転数を超えて回転した際、オイルＯは、遠心力によって優先的に各第２側孔５２から排出されそうになる。 As shown in FIG. 3 , the plurality of first side holes 22 and the plurality of second side holes 52 are connected via the first threaded portion 21 and the second threaded portion 51 . Thereby, the flow path 12 through which the oil O can pass is secured. The flow path 12 is the coolant supply hole 33 . Further, the oil O flowing into the shaft 1 from the opening 201 includes the oil O1 that flows directly downstream beyond the second side hole 52 and the oil O1 that flows toward the flow path 12 via the second side hole 52. O2 is present. In this state, when the rotor 30 rotates over a predetermined number of revolutions, the oil O is likely to be preferentially discharged from the second side holes 52 due to centrifugal force.
　しかしながら、各第２側孔５２と各第１側孔２２とが中心軸Ｊ方向にズレて配置されているため、流路１２に向かうオイルＯ２の流れが抑制される。そして、オイルＯ２の流れが抑制された分、オイルＯ１の流れを十分に確保することができる。これにより、ロータ３０の回転数の大小に関わらず、オイルＯ２でステータ４０に対する冷却効率を向上させつつ、オイルＯ１でロータ３０に対する冷却効率も十分に向上させることができる。また、オイルＯ１をベアリング３５の潤滑油として十分に機能させることもできる。 However, since the second side holes 52 and the first side holes 22 are displaced in the direction of the central axis J, the flow of the oil O2 toward the flow path 12 is suppressed. Since the flow of the oil O2 is suppressed, the flow of the oil O1 can be sufficiently secured. As a result, regardless of the rotational speed of the rotor 30, the cooling efficiency of the stator 40 can be improved by the oil O2, and the cooling efficiency of the rotor 30 can be sufficiently improved by the oil O1. Also, the oil O1 can sufficiently function as a lubricating oil for the bearings 35 .
　また、上流側から見たとき、シャフト１の回転方向と、第１ネジ部２１および第２ネジ部５１のネジ方向とが同一である。例えば、上流側から見たとき、シャフト１の回転方向が時計回り（右回り）の場合、第１ネジ部２１および第２ネジ部５１のネジ方向は、右ネジの方向となる。これにより、オイルＯ２が第２側孔５２から第１側孔２２へ円滑に通過することができる。　図４に示すように、第２ネジ５１（雄ネジ）の外径φＤ５１は、第１ネジ２１（雌ネジ）の谷の径φＤ２１の８０％以上９５％以下であるのが好ましく、８０％以上９０％以下であるのがより好ましい。これにより、第１ネジ部２１と第２ネジ部５１との嵌め合い状態を十分に維持しつつ、第１ネジ部２１と第２ネジ部５１との間をできる限り広げて、オイルＯ２を容易に通過させることができる。 Further, when viewed from the upstream side, the rotation direction of the shaft 1 and the screw directions of the first threaded portion 21 and the second threaded portion 51 are the same. For example, when the rotation direction of the shaft 1 is clockwise (right-handed) when viewed from the upstream side, the screw directions of the first threaded portion 21 and the second threaded portion 51 are right-handed. This allows the oil O2 to smoothly pass from the second side hole 52 to the first side hole 22 . As shown in FIG. 4, the outer diameter φD51 of the second screw 51 (male screw) is preferably 80% or more and 95% or less of the root diameter φD21 of the first screw 21 (female screw). More preferably, it is 90% or less. As a result, the space between the first threaded portion 21 and the second threaded portion 51 is widened as much as possible while the fitting state between the first threaded portion 21 and the second threaded portion 51 is sufficiently maintained, thereby facilitating the flow of the oil O2. can be passed to
　また、第２ネジ５１（雄ネジ）のネジ山５１１と第１ネジ２１（雌ネジ）のネジ溝２１１とは、径方向から見たときの側面視で、大きさまたは形状のうち少なくとも１つが異なる。本実施形態では、ネジ山５１１の形状およびネジ溝２１１の形状は、いずれも、三角形であるが、ネジ山５１１の方が、ネジ溝２１１よりも小さい。これによっても、第１ネジ部２１と第２ネジ部５１との間をできるだけ広げて、オイルＯ２の容易な通過に寄与する。このように、各ネジの大きさまたは形状のうち少なくとも１つを適宜設計変更することにより、オイルＯ２の流量を調整することができる。 In addition, the thread ridge 511 of the second screw 51 (male screw) and the screw groove 211 of the first screw 21 (female screw) have at least one size or shape in side view when viewed from the radial direction. different. In this embodiment, both the shape of the thread 511 and the shape of the thread groove 211 are triangular, but the thread 511 is smaller than the thread groove 211 . This also widens the space between the first threaded portion 21 and the second threaded portion 51 as much as possible, contributing to easy passage of the oil O2. Thus, the flow rate of the oil O2 can be adjusted by appropriately changing the design of at least one of the size and shape of each screw.
　前述したように、第２ネジ部５１の第１ネジ部２１に対する捩じ込み量を変更することにより、第１側孔２２と第２側孔５２との離間距離ＳＤを調整することができる。離間距離ＳＤが小さければ小さいほど、第２側孔５２から第１側孔２２へのオイルＯの流量を増加させることができる。反対に、離間距離ＳＤが大きければ大きいほど、第２側孔５２から第１側孔２２へのオイルＯ２の流量を減少させることができる。従って、離間距離ＳＤの大小によっても、オイルＯ２の流量を調整することができる。　なお、シャフト本体２および円筒体５の構成材料としては、特に限定されず、例えば、金属材料や樹脂材料等の硬質材料を用いることができる。 As described above, the separation distance SD between the first side hole 22 and the second side hole 52 can be adjusted by changing the amount of screwing of the second threaded portion 51 into the first threaded portion 21 . The smaller the separation distance SD, the more the flow rate of the oil O from the second side hole 52 to the first side hole 22 can be increased. Conversely, the larger the clearance SD is, the more the flow rate of the oil O2 from the second side hole 52 to the first side hole 22 can be reduced. Therefore, the flow rate of the oil O2 can also be adjusted depending on the distance SD. The materials for the shaft body 2 and the cylindrical body 5 are not particularly limited, and for example, hard materials such as metal materials and resin materials can be used.
　以上、本発明の回転電機および駆動装置を図示の実施形態について説明したが、本発明は、これに限定されるものではなく、回転電機および駆動装置を構成する各部は、同様の機能を発揮し得る任意の構成のものと置換することができる。また、任意の構成物が付加されていてもよい。　また、第２側孔５２の中心軸Ｊ方向における配置位置や配置数が異なる複数種の円筒体５を予め用意してもよい。この場合、例えばシャフト１が搭載される回転電機１０の種類等の諸条件に応じて、適当な円筒体５を複数種の円筒体５の中から選択して、シャフト本体２に取り付けることができる。　また、円筒体５は、連続した１つの部材で構成されているが、これに限定されず、例えば、中心軸Ｊ方向に沿って、少なくとも２つに分割された分割体を含む構成となっていてもよい。 As described above, the rotating electric machine and the drive device of the present invention have been described with reference to the illustrated embodiments, but the present invention is not limited to this, and each part constituting the rotating electric machine and the drive device performs the same function. can be substituted with any configuration available. Moreover, arbitrary components may be added. Also, a plurality of types of cylindrical bodies 5 having different arrangement positions and numbers of the second side holes 52 in the direction of the central axis J may be prepared in advance. In this case, an appropriate cylindrical body 5 can be selected from a plurality of types of cylindrical bodies 5 and attached to the shaft main body 2 according to various conditions such as the type of the rotating electric machine 10 on which the shaft 1 is mounted. . Further, the cylindrical body 5 is composed of one continuous member, but is not limited to this, and for example, has a configuration including a divided body divided into at least two along the direction of the central axis J. may
　１　　　　シャフト　２　　　　シャフト本体　２０１　　開口部　２０２　　端面　２１　　　第１ネジ部　２１１　　ネジ山　２２　　　第１側孔　２３１　　内周面　２３３　　小径部　２３４　　小径部　２３５　　大径部　５　　　　円筒体　５０１　　外周面　５１　　　第２ネジ部　５１１　　ネジ溝　５２　　　２側孔　５３　　　フランジ部　１０　　　回転電機　１２　　　流路　３０　　　ロータ　３２　　　ロータ本体　３３　　　冷媒供給孔　３４　　　ベアリング　３５　　　ベアリング　４０　　　ステータ　４１　　　ステータコア　４２　　　コイルアセンブリ　４２ｃ　　コイル　５０　　　ステータ冷媒供給部　５０ａ　　供給口　６０　　　伝達装置　６２　　　減速装置　６３　　　差動装置　６３ａ　　リングギヤ　６４　　　車軸　７１　　　ポンプ　７２　　　クーラ　８０　　　ハウジング　８１　　　モータハウジング　８１ａ　　周壁部　８１ｂ　　隔壁部　８１ｃ　　蓋部　８１ｄ　　隔壁開口　８２　　　ヤハウジング　９０　　　冷媒流路　９１　　　第１流路部　９２　　　第２流路部　９３　　　第３流路部　９４　　　接続流路部　９５　　　シャフト流路部　９６　　　径方向流路部　９７　　　ガイド流路部　９８　　　軸方向流路部　１００　　駆動装置　φＤ２１　径　φＤ５１　外径　Ｊ　　　　中心軸（軸）　ＳＤ　　　離間距離　Ｏ　　　　オイル　Ｏ１　　　オイル　Ｏ２　　　オイル 1 Shaft 2 Shaft main body 201 Opening 202 End face 21 First screw part 211 Screw thread 22 First side hole 231 Inner peripheral surface 233 Small diameter part 234 Small diameter part 235 Large diameter part 5 Cylindrical body 501 Outer peripheral surface 51 Second screw part 511 Groove 52 2 side hole 53 Flange portion 10 Rotating electric machine 12 Flow path 30 Rotor 32 Rotor main body 33 Coolant supply hole 34 Bearing 35 Bearing 40 Stator 41 Stator core 42 Coil assembly 42c Coil 50 Stator coolant supply part 50a Transmission device 602 63 Differential device 63a Ring gear 64 Axle 71 Pump 72 Cooler 80 Housing 81 Motor housing 81a Peripheral wall portion 81b Partition wall portion 81c Lid portion 81d Partition wall opening 82 Rear housing 90 Refrigerant passage portion 91 First passage portion 92 3 Second passage portion 9 3 channel part 94 connection channel part 95 shaft channel part 96 radial direction channel part 97 guide channel part 98 axial direction channel part 100 drive device φD21 diameter φD51 outer diameter J central axis (axis) SD separation distance O oil O1 Oil O2 Oil

Claims (7)

  1. 　内部に冷媒が流通可能なシャフトを有し、該シャフトを回転中心として回転可能なロータと、
    　該ロータの径方向外側に位置するステータとを備え、
    　前記シャフトは、
    　内周面に設けられた第１ネジ部と、径方向に貫通する複数の第１側孔とを有する円筒状のシャフト本体と、
    　外周面に設けられた第２ネジ部と、径方向に貫通する複数の第２側孔とを有する円筒体とを備え、
    　前記第２ネジ部を回転により前記第１ネジ部に嵌め合わせることにより、前記円筒体を前記シャフト本体の軸方向一方側に取り付けた取付状態で、前記複数の第２側孔が前記複数の第１側孔より軸方向一方側に位置し、
    　前記複数の第１側孔と前記複数の第２側孔とが、前記第１ネジ部と前記第２ネジ部との間を介して繋がり、前記冷媒が通過可能な流路として機能することを特徴とする回転電機。     a rotor having a shaft through which a coolant can flow, and rotatable around the shaft;
    a stator positioned radially outward of the rotor,
    The shaft is
    a cylindrical shaft body having a first threaded portion provided on an inner peripheral surface and a plurality of first side holes penetrating in a radial direction;
    A cylindrical body having a second threaded portion provided on the outer peripheral surface and a plurality of second side holes penetrating in the radial direction,
    By rotating the second threaded portion to fit the first threaded portion, the plurality of second side holes are aligned with the plurality of second side holes in a mounting state in which the cylindrical body is mounted on one side of the shaft body in the axial direction. Located on one side in the axial direction from the 1 side hole,
    The plurality of first side holes and the plurality of second side holes are connected via between the first screw portion and the second screw portion, and function as a flow path through which the refrigerant can pass. Rotating electric machine characterized by:
  2. 　前記円筒体は、その軸方向一方側の端部に位置し、径方向外側に向かって突出するフランジ部であって、前記取付状態で、前記シャフト本体に接触するフランジ部を有する請求項１に記載の回転電機。 2. The cylinder according to claim 1, wherein the cylindrical body has a flange portion located at one end in the axial direction thereof and protruding radially outward, the flange portion coming into contact with the shaft body in the mounted state. Rotating electric machine described.
  3. 　前記第１ネジ部は、雌ネジであり、前記第２ネジ部は、雄ネジであり、
    　前記雄ネジの外径は、前記雌ネジの谷の径の８０％以上９５％以下である請求項１または２に記載の回転電機。     The first threaded portion is a female thread, the second threaded portion is a male thread,
    The rotary electric machine according to claim 1 or 2, wherein the outer diameter of the male thread is 80% or more and 95% or less of the root diameter of the female thread.
  4. 　前記第１ネジ部は、雌ネジであり、前記第２ネジ部は、雄ネジであり、
    　前記雄ネジのネジ山と前記雌ネジのネジ溝とは、径方向から見たときの大きさまたは形状のうち少なくとも１つが異なる請求項１～３のいずれか１項に記載の回転電機。     The first threaded portion is a female thread, the second threaded portion is a male thread,
    The electric rotating machine according to any one of claims 1 to 3, wherein the screw thread of the male screw and the screw groove of the female screw differ in at least one of size and shape when viewed in the radial direction.
  5. 　軸方向一方側から見たとき、前記シャフトの回転方向と、前記第１ネジ部および前記第２ネジ部のネジ方向とが同一である請求項１～４のいずれか１項に記載の回転電機。 The electric rotating machine according to any one of claims 1 to 4, wherein when viewed from one side in the axial direction, the rotating direction of the shaft is the same as the threading direction of the first threaded portion and the second threaded portion. .
  6. 　前記第２ネジ部の前記第１ネジ部に対する回転量を変更することにより、前記第２側孔と前記第１側孔との軸方向における離間距離が調整可能である請求項１～５のいずれか１項に記載の回転電機。 6. The distance between the second side hole and the first side hole in the axial direction can be adjusted by changing the amount of rotation of the second threaded part with respect to the first threaded part. 1. The rotary electric machine according to claim 1.
  7. 　車両に搭載され、車軸を回転させる駆動装置であって、
    　請求項１～６のいずれか１項に記載の回転電機と、
    　前記回転電機に接続され、前記ロータの回転を前記車軸に伝達する伝達装置と、
    　前記回転電機および前記伝達装置を収容するハウジングと、
    　前記ハウジング内に設けられ、前記回転電機の前記シャフト内および前記ステータに冷媒を供給する冷媒流路とを備えることを特徴とする駆動装置。     A driving device mounted on a vehicle for rotating an axle,
    a rotating electric machine according to any one of claims 1 to 6;
    a transmission device that is connected to the rotating electrical machine and that transmits rotation of the rotor to the axle;
    a housing that accommodates the rotating electric machine and the transmission device;
    A driving device, comprising: a coolant passage provided in the housing for supplying a coolant to the shaft and the stator of the rotating electric machine.
PCT/JP2021/022349 2021-02-24 2021-06-11 Rotating electric machine and drive device WO2022180875A1 (en)

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5386414A (en) * 1976-11-30 1978-07-29 Sp K Buyuro Enerugohimumashi Electric machine which is cooled by lowwtemperature fluid
WO2011132784A1 (en) * 2010-04-23 2011-10-27 株式会社Ihi Rotating machine
JP2013051805A (en) * 2011-08-31 2013-03-14 Toyota Motor Corp Cooling structure of rotary electric machine
JP2015226363A (en) * 2014-05-27 2015-12-14 富士重工業株式会社 Electric-motor cooling apparatus
JP2016014445A (en) * 2014-07-03 2016-01-28 Ntn株式会社 In-wheel motor driving gear

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5386414A (en) * 1976-11-30 1978-07-29 Sp K Buyuro Enerugohimumashi Electric machine which is cooled by lowwtemperature fluid
WO2011132784A1 (en) * 2010-04-23 2011-10-27 株式会社Ihi Rotating machine
JP2013051805A (en) * 2011-08-31 2013-03-14 Toyota Motor Corp Cooling structure of rotary electric machine
JP2015226363A (en) * 2014-05-27 2015-12-14 富士重工業株式会社 Electric-motor cooling apparatus
JP2016014445A (en) * 2014-07-03 2016-01-28 Ntn株式会社 In-wheel motor driving gear

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