CN112534690A - Motor - Google Patents

Abstract

One aspect of the motor of the present invention includes: a rotor having a motor shaft disposed along a central axis extending in one direction; a stator that faces the rotor in a radial direction with a gap therebetween; and a housing having a housing portion that houses the rotor and the stator and is capable of storing oil. The housing has a cylindrical portion supporting the stator from a radially outer side. The cylinder portion has a cooling flow path through which a refrigerant flows. The housing has a fin portion protruding into the housing.

Description

Motor

Technical Field

The present invention relates to a motor. The present application claims priority based on japanese patent application No. 2018-148692 filed on 2018, 08-month 07 and japanese patent application No. 2018-148693 filed on 2018, 08-month 07, the contents of which are incorporated herein by reference.

Background

A rotating electrical machine including a housing that stores a lubricating fluid for lubricating and cooling a stator, a rotor, and the like is known. For example, patent document 1 describes a rotating electric machine mounted on a vehicle.

Documents of the prior art

Patent document

Patent document 1: japanese patent laid-open publication No. 2013-055728

Disclosure of Invention

Problems to be solved by the invention

The lubricating fluid is guided to the outside of the casing and cooled, for example. However, in this case, a flow path for leading out the lubricating fluid from the casing to the outside needs to be provided, which causes a problem that the structure of the rotating electric machine becomes complicated. Further, in order to ensure the airtightness of the casing, it is necessary to seal a connection portion between the casing and a flow path for guiding the lubricating fluid to the outside with high accuracy, and thus the number of steps and cost for manufacturing the rotating electric machine may increase.

The present invention has been made in view of the above circumstances, and an object thereof is to provide a motor capable of appropriately cooling a stator and oil stored in a case with a simple structure.

Means for solving the problems

One aspect of the motor of the present invention includes: a rotor having a motor shaft disposed along a central axis extending in one direction; a stator that faces the rotor in a radial direction with a gap interposed therebetween; and a housing having a housing portion that houses the rotor and the stator and is capable of storing oil. The housing has a cylindrical portion supporting the stator from a radially outer side. The cylinder portion has a cooling flow path through which a refrigerant flows. The housing has a fin portion protruding into the housing.

The effects of the invention are as follows.

According to one aspect of the present invention, in the motor, the stator and the oil stored in the housing can be appropriately cooled with a simple configuration.

Drawings

Fig. 1 is a perspective view showing a motor of the present embodiment.

Fig. 2 is a view showing the motor of the present embodiment, and is a sectional view II-II in fig. 1.

Fig. 3 is a view of the pump section of the present embodiment as viewed from the other axial side.

Fig. 4 is a view of the water jacket of the present embodiment as viewed from one axial side.

Fig. 5 is a perspective view showing a part of the water cooling jacket of the present embodiment.

Fig. 6 is a view showing a part of the motor of the present embodiment, and is a partially enlarged view in fig. 2.

Fig. 7 is a perspective view showing the cooling flow path of the present embodiment.

Fig. 8 is a schematic configuration diagram schematically showing a driving device mounted with the motor of the present embodiment.

Detailed Description

The Z-axis direction shown in each figure is a vertical direction Z in which the positive side is the upper side and the negative side is the lower side. In the present embodiment, the vertical direction Z is the vertical direction of each drawing. In the following description, the vertical upper side is simply referred to as "upper side", and the vertical lower side is simply referred to as "lower side".

As shown in fig. 1 and 2, the motor 1 of the present embodiment includes a housing 10, a rotor 20 having a motor shaft 20a disposed along a central axis J1 extending in one direction, a rotation detecting unit 80, a stator 30, a pump unit 40, and bearings 70 and 71.

As shown in fig. 2, the center axis J1 extends in the left-right direction in fig. 2. That is, in the present embodiment, the left-right direction in fig. 2 corresponds to one direction. The Y-axis direction shown in each figure is a direction parallel to the central axis J1. In the following description, a direction parallel to the axial direction of the center axis J1 is simply referred to as "axial direction Y", a radial direction about the center axis J1 is simply referred to as "radial direction", and a circumferential direction about the center axis J1 is simply referred to as "circumferential direction R". The axial direction Y is a direction orthogonal to the vertical direction Z. The left side in fig. 2 in the axial direction Y, that is, the positive side in the Y axis direction, is referred to as "one axial side", and the right side in fig. 2 in the axial direction Y, that is, the negative side in the Y axis direction, is referred to as "the other axial side". The X-axis direction shown in each drawing is a direction orthogonal to both the axial direction Y and the vertical direction Z. In the following description, a direction parallel to the X-axis direction is referred to as a "width direction X".

The case 10 includes a main body 11, a lid 13, a water jacket 60, and a plate member 12. In the present embodiment, the body 11, the lid 13, the water jacket 60, and the plate member 12 are independent members. The body 11 has a bottomed tubular shape with one side opening in the axial direction. The main body 11 has a bottom portion 11a, a second cylindrical portion 11b, a bearing holding portion 11c, and a wiring housing portion 11 e. The bottom 11a has a circular ring plate shape expanding in the radial direction.

The second cylindrical portion 11b is cylindrical and extends from the radially outer edge of the bottom portion 11a to one axial side. In the present embodiment, the second tube portion 11b has a cylindrical shape centered on the central axis J1. The second cylindrical portion 11b has a flow path formation portion 11 d. The flow passage forming portion 11d is a portion of the radially inner surface of the second cylindrical portion 11b that faces the inside of the cooling flow passage 90 described below. The bearing holding portion 11c is cylindrical and protrudes from the radially inner edge portion of the bottom portion 11a to one axial side. The bearing holding portion 11c holds the bearing 71 on the inner peripheral surface.

The wiring housing 11e is provided at an upper portion of the second tube 11 b. The wiring housing 11e protrudes upward from the radially outer surface of the second tube 11 b. In the present embodiment, the wiring housing 11e has a box shape with one side opening in the axial direction. The wiring housing portion 11e has a trapezoidal shape when viewed in the axial direction. In the present embodiment, the opening on one axial side of the body 11 is formed by the opening on one axial side of the second tube 11b and the opening on one axial side of the wiring housing 11 e. The wiring housing portion 11e has a connector wall portion 11f and a ceiling wall portion 11 g.

The connector wall portion 11f is a wall portion located on the other axial side among wall portions constituting the box-shaped wiring housing portion 11 e. The connector wall 11f is provided with a plurality of connectors 100. As shown in fig. 1, the plurality of connectors 100 project from the connector wall portion 11f toward the other side in the axial direction. The plurality of connectors 100 are arranged in the width direction X. The connector 100 is provided with three, for example. The top wall portion 11g is a wall portion located on the upper side among wall portions constituting the box-shaped wiring housing portion 11 e. As shown in fig. 2, the top wall portion 11g is provided with a through hole 11h penetrating the top wall portion 11g in the vertical direction Z. The through hole 11h is closed by fixing the plate member 12 to the top wall portion 11g with a screw or the like.

As shown in fig. 2, the lid 13 is attached to one axial side of the body 11. The lid 13 closes the opening of the body 11 on one axial side. The housing portion 17 surrounded by the body portion 11 and the lid portion 13 is configured by fixing the body portion 11 and the lid portion 13 to each other. That is, the housing 10 has the housing 17. The housing 17 can house the rotor 20 and the stator 30 and can store oil O. The oil O is stored in the lower region in the vertical direction inside the housing portion 17. In the present specification, the "lower region in the vertical direction inside the housing portion" includes a portion located below the center in the vertical direction Z inside the housing portion 17.

The liquid surface OS of the oil O stored in the housing portion 17 fluctuates due to the pumping of the oil O by the pump portion 40, but is disposed below the rotor 20 at least when the rotor 20 rotates. This can prevent the oil O from becoming rotational resistance of the rotor 20 when the rotor 20 rotates.

As the oil O, in order to exhibit functions of a lubricating oil and a cooling oil, it is preferable to use the same oil as an Automatic Transmission lubricating oil (ATF) having a low viscosity.

The lid 13 has a side wall portion 13d, an outer cylinder portion 13e, a bearing holding portion 13g, and a plug portion 14. The side wall portion 13d is located on one axial side of the stator 30 and radially expands. The side wall portion 13d covers one axial side of the stator 30. That is, the cover 13 covers one axial side of the stator 30. The side wall portion 13d is provided with a recess 13i recessed from a surface on one axial side of the side wall portion 13d toward the other axial side. A first through hole 13j that penetrates the bottom of the recess 13i in the axial direction Y is provided in the bottom of the recess 13 i. The first through hole 13j connects the interior of the pump chamber 46 described below with the interior of the housing 10. The outer cylindrical portion 13e has a cylindrical shape extending from the radially outer edge portion of the side wall portion 13d toward the other axial side.

The lid 13 is provided with a pump chamber 46. The pump chamber 46 is configured by the plug portion 14 closing the recess 13i provided in the side wall portion 13d from one axial side. The plug portion 14 is fixed to one axial surface of the side wall portion 13d by a screw, for example. An annular seal 14a is disposed between the side wall portion 13d and the plug portion 14 in the axial direction. Although not shown, the seal 14a surrounds the recess 13i when viewed in the axial direction. This can suppress leakage of the oil O in the pump chamber 46 to the outside of the housing 10. The central shaft J1 passes through the pump chamber 46. As shown in fig. 3, the pump chamber 46 has a circular outer shape when viewed in the axial direction. The pump chamber 46 houses an internal gear 43 and an external gear 42 described below.

The pump chamber 46 is provided with a suction port 44 through which the oil O can be sucked from the inside of the housing portion 17 into the pump chamber 46, and a discharge port 45 through which the oil O can be discharged from the inside of the pump chamber 46. The suction port 44 and the discharge port 45 are circular, for example. The suction port 44 is disposed below the discharge port 45. The suction port 44 is disposed lower than the center axis J1. The discharge port 45 is disposed above the center axis J1.

Although not shown, the plug portion 14 has a portion inserted into the recess 13 i. As shown in fig. 3, a connection oil passage 13n into which the oil O from the discharge port 45 flows is provided in a portion of the plug body portion 14 inserted into the recess 13 i. The connection oil passage 13n is connected to a second oil passage 20b described below via a connection port 13 p. The connection port 13p is circular, for example.

As shown in fig. 2, the lid portion 13 has a first oil passage 13 a. In the present embodiment, the first oil passage 13a is provided in the side wall portion 13 d. More specifically, the first oil passage 13a is provided in a lower portion of the side wall portion 13 d. The first oil passage 13a has a vertical direction extending portion 13k and an axial direction extending portion 13 m.

The vertical extending portion 13k is a portion extending upward from the lower end of the side wall portion 13 d. The upper end of the vertical extending portion 13k is connected to the pump chamber 46 on the other axial side of the pump chamber 46. A portion of the pump chamber 46 connected to the vertical extending portion 13k is the suction port 44. A seal bolt 13c is provided at the lower end of the vertical extending portion 13 k. The seal bolt 13c seals and seals the lower end of the vertical extending portion 13 k. This can suppress leakage of the oil O in the housing 17 to the outside of the case 10.

The axially extending portion 13m extends axially to one side from the surface on the other axial side of the side wall portion 13d, and is connected to the vertically extending portion 13 k. The end of the axially extending portion 13m on the other axial side is an opening 13h that opens into the housing 17. That is, the first oil passage 13a has an opening 13 h. Thereby, the first oil passage 13a is exposed and opened in the housing 17, and connects the interior of the housing 17 to the suction port 44.

In the present embodiment, the opening 13h is located below the liquid level OS of the oil O stored in the storage portion 17. Thus, the opening 13h is exposed to the oil O stored in the housing 17. In the present embodiment, the pump section 40 is driven, and the oil O in the housing section 17 flows into the first oil passage 13a from the opening section 13 h. The oil O flowing into the first oil passage 13a is sent to the rotor 20 and the stator 30 via the pump chamber 46, the connecting oil passage 13n, and a second oil passage 20b described below.

A filter 13b is provided in the first oil passage 13 a. In the present embodiment, the filter 13b is provided inside a portion of the vertically extending portion 13k that is located above the axially extending portion 13 m. The oil O delivered from the inside of the housing 17 to the pump chamber 46 via the first oil passage 13a passes through the filter 13 b. The filter 13b can remove foreign matter contained in the oil O transferred from the storage portion 17 to the pump chamber 46. Therefore, the entry of foreign matter into the pump chamber 46 can be suppressed.

The bearing holding portion 13g is provided at a radially central portion of the side wall portion 13 d. The bearing holding portion 13g holds the bearing 70 inside. That is, the cover 13 holds the bearing 70. A pump chamber 46 is provided on one axial side of the bearing holding portion 13 g.

As shown in fig. 2, 4, and 5, the water jacket 60 is a tubular member surrounding the center axis J1 as a whole. The water jacket 60 is part of the housing 10. The outer peripheral surface of the water jacket 60 contacts the inner peripheral surface of the second tube 11b of the body 11. The stator 30 is fixed to the inner circumferential surface of the water jacket 60.

The water jacket 60 includes a first tube 61, a mounting portion 62, and a fin 63. That is, the housing 10 includes the first cylindrical portion 61, the mounting portion 62, and the fin portion 63. As shown in fig. 2, the first cylindrical portion 61 supports the stator 30 from the radially outer side. In the present embodiment, the first cylindrical portion 61 is cylindrical and opens on both sides in the axial direction Y about the central axis J1. The first cylindrical portion 61 is located radially inward of the second cylindrical portion 11 b. The outer peripheral surface of the first cylindrical portion 61 is the outer peripheral surface of the water jacket 60. A groove 61a extending in the circumferential direction R is provided in the outer circumferential surface of the first cylindrical portion 61. Although not shown, the groove 61a has a C-shape when viewed in the axial direction. The groove 61a constitutes a cooling flow path 90 described below.

In the present embodiment, the first tube 61 of the water jacket 60 and the second tube 11b of the body 11 overlap in the radial direction, and form a tube 10a that supports the stator 30 from the outside in the radial direction. That is, in the present embodiment, the housing 10 has the cylindrical portion 10a, and the cylindrical portion 10a has the first cylindrical portion 61 and the second cylindrical portion 11b located radially outward of the first cylindrical portion 61. The cylindrical portion 10a has a cylindrical shape with one side opening in the axial direction. The opening of the cylindrical portion 10a on one axial side is closed by the lid 13. The cylindrical portion 10a constitutes a part of the housing portion 17.

The mounting portion 62 is in the form of a flange extending radially outward from one axial end of the first tube portion 61. As shown in fig. 4, the mounting portion 62 surrounds the center axis J1. The mounting portion 62 has a projecting portion 62a projecting in a trapezoidal shape on the upper side. The protruding portion 62a is a portion of the mounting portion 62 located on the upper side. The protruding portion 62a is provided with a hole 62c that penetrates the protruding portion 62a in the axial direction Y. As shown in fig. 2, the hole 62c faces the opening of the wiring housing 11e on one axial side. The attachment portion 62 is sandwiched between the opening edge portion of the body portion 11 and the opening edge portion of the lid portion 13 in the axial direction Y.

As shown in fig. 4, the mounting portion 62 is provided with a plurality of mounting holes 62b at intervals in the circumferential direction R. The mounting hole 62b penetrates the mounting portion 62 in the axial direction Y. The screws are inserted through the respective mounting holes 62b from one axial side. The screw inserted into the mounting hole 62b is inserted through a flange provided in the lid 13 and screwed into an opening edge of the body 11. Thereby, the water jacket 60 is fastened and fixed to the body 11 together with the lid 13 by screws.

As shown in fig. 5, the fin portion 63 protrudes from one axial end of the first tube portion 61 toward one axial side. As shown in fig. 2, the fin portion 63 protrudes toward the cover 13 in one axial direction and faces the cover 13 in the axial direction Y. As shown in fig. 5, in the present embodiment, the plurality of fin portions 63 are provided in the circumferential direction R around the central axis J1. The fin 63 has, for example, a substantially rectangular plate shape with its plate surface facing the circumferential direction R.

In the present embodiment, the plurality of fin portions 63 are provided in a lower portion of the first tube portion 61. The plurality of fin portions 63 are located below the center axis J1. The plurality of fin portions 63 are arranged at equal intervals in an arc shape passing through the lowermost end of the cylindrical first tube portion 61, for example. Among the plurality of fin portions 63, the fin portion 63 located on the one side in the circumferential direction and the fin portion 63 located on the other side in the circumferential direction are disposed at the same position in the vertical direction Z, for example.

As shown in fig. 2, the fin 63 protrudes into the housing 17. The fin 63 is located below the liquid surface OS of the oil O stored in the housing 17. That is, the fin portion 63 is immersed in the oil O stored in the housing portion 17. The fin 63 projects to one axial side from the coil end 32a of the stator 30 described below. The distance between the end of the fin 63 on one axial side in the axial direction Y and the cover 13 is shorter than the distance between the coil end 32a and the cover 13 in the axial direction Y.

In the present embodiment, at least a part of the fin 63 faces the opening 13 h. In the present specification, the phrase "at least a part of the fin portion faces the opening", and at least a part of at least one fin portion may face the opening. In the present embodiment, among the plurality of fin portions 63, a portion of the plurality of fin portions 63 provided at the lower end portion of the first cylindrical portion 61 faces the opening 13 h.

The rotor 20 has a motor shaft 20a, a rotor core 22, a magnet 23, a first end plate 24, and a second end plate 25. The motor shaft 20a has a motor shaft main body 21 and a mounting member 50. A rotor core 22 is attached to the motor shaft main body 21. The portion of the motor shaft main body 21 where the rotor core 22 is attached is a large diameter portion 21 a.

One end of the motor shaft main body 21 in the axial direction is rotatably supported by the bearing 70. Further, a portion of the motor shaft main body 21 located on the other axial side than the rotor core 22 is rotatably supported by the bearing 71. Therefore, the bearings 70 and 71 rotatably support the motor shaft 20 a. The bearings 70 and 71 are, for example, ball bearings. The other axial end of the motor shaft body 21 is an output shaft 21b that penetrates the bottom portion 11a in the axial direction Y and protrudes outside the housing 10. The output shaft portion 21b has an outer diameter smaller than that of the large diameter portion 21 a.

The motor shaft main body 21 has a flange portion 21 f. The flange 21f is provided on the other axial side of the rotor core 22 in the motor shaft main body 21. The flange 21f projects radially outward from the large-diameter portion 21a of the motor shaft main body 21 to which the rotor core 22 is fixed. The flange portion 21f has an annular plate shape. The motor shaft main body 21 has a hole 21g extending from one axial end of the motor shaft main body 21 to the other axial end. The hole 21g is a bottomed hole that opens on one side in the axial direction. That is, the end of the hole 21g on the other axial side is closed.

The mounting member 50 is fixed to one axial side of the motor shaft main body 21. The mounting member 50 is fitted into and fixed to the hole 21 g. The mounting member 50 has a cylindrical shape open on both sides in the axial direction. In the present embodiment, the mounting member 50 has a cylindrical shape centered on the central axis J1. The mounting member 50 extends to one axial side of the motor shaft main body 21 and passes through the first through hole 13 j.

The mounting member 50 has a fitting portion 51 and a fixing portion 52. The fitting portion 51 is a portion fitted in the hole 21 g. The fitting portion 51 is fixed to the inner peripheral surface of one axial end of the hole 21g and extends from the inside of the hole 21g to one axial end of the motor shaft main body 21. The end portion of the fitting portion 51 on one axial side is inserted into the first through hole 13 j. That is, at least a part of the fitting portion 51 is inserted into the first through hole 13 j. Therefore, the gap between the outer peripheral surface of the mounting member 50 and the inner peripheral surface of the first through-hole 13j in the radial direction can be increased. Thus, even when the position of the mounting member 50 is displaced in the radial direction by vibration or the like, the mounting member 50 can be prevented from contacting the inner peripheral surface of the first through hole 13 j.

The fixing portion 52 is located on one axial side of the fitting portion 51. The fixing portion 52 is connected to one axial end of the fitting portion 51. The outer diameter of the fixing portion 52 is larger than the outer diameter of the fitting portion 51 and smaller than the inner diameter of the first through hole 13 j. The fixing portion 52 is inserted into the pump chamber 46. The inner diameter of the fitting portion 51 is, for example, the same as the inner diameter of the fixing portion 52.

An external gear 42 described below is fixed to the mounting member 50. In the present embodiment, the external gear 42 is fixed to the radially outer surface of the fixing portion 52. More specifically, as shown in fig. 3, the fixing portion 52 is fitted and fixed to a fixing hole portion 42b that penetrates the external gear 42 in the axial direction Y. As described above, according to the present embodiment, the fitting portion 51 having an outer diameter smaller than the outer diameter of the fixing portion 52 is fitted to the hole portion 21g, and the external gear 42 is fixed to the fixing portion 52 having an outer diameter larger than the outer diameter of the fitting portion 51. Therefore, the inner diameter of the hole portion 21g can be made smaller than the inner diameter of the fixing hole portion 42b of the external gear 42. This makes it easy to reduce the inner diameter of the hole 21g, and can suppress a decrease in the rigidity of the motor shaft 20 a.

As shown in fig. 2, the motor shaft 20a has a second oil passage 20b provided inside the motor shaft 20 a. The second oil passage 20b is a bottomed hole portion recessed and extending from an end portion on one axial side of the motor shaft 20a to the other axial side. The second oil passage 20b is open on one axial side. The second oil passage 20b extends from an end portion on one axial side of the mounting member 50 to an end portion on the other axial side. The second oil passage 20b is formed by connecting the inside of the mounting member 50 and the hole 21g in the axial direction Y. That is, the radially inner side surface of the mounting member 50 constitutes a part of the radially inner side surface of the second oil passage 20 b.

In the present embodiment, in a cross section orthogonal to the axial direction Y, the inner edge of the second oil passage 20b is circular about the central axis J1. The inner diameter of the portion of the second oil passage 20b provided in the mounting member 50 is smaller than the inner diameter of the portion of the second oil passage 20b provided in the motor shaft 20 a. That is, the inner diameter of the mounting member 50 is smaller than the inner diameter of the hole portion 21 g. Since the opening on one axial side of the mounting member 50 is connected to the connection port 13p, the second oil passage 20b is connected to the connection oil passage 13 n. That is, the second oil passage 20b opens to the connection oil passage 13n at one axial end of the motor shaft 20 a. The second oil passage 20b is connected to the discharge port 45 via a connection oil passage 13 n.

The motor shaft 20a has second through holes 26a to 26d that connect the second oil passage 20b to the outer peripheral surface of the motor shaft 20 a. The second through holes 26a to 26d extend in the radial direction. The second through holes 26a and 26b are provided in the large diameter portion 21 a. The second through holes 26a and 26b are disposed between the flange 21f and the nut 27 that fixes the first end plate 24 and the second end plate 25 in the axial direction Y. The radially outer end of the second through hole 26a opens into the gap between the first end plate 24 and the rotor core 22 in the axial direction Y. The second end plate 25 of the second through hole 26b on the outer side in the radial direction opens into the gap between the rotor core 22 and the axial direction Y.

The radially outer end of the second through hole 26c opens on the radially outer surface of the motor shaft 20a at a portion between the bearing 70 and a detection target 81 described below in the axial direction Y. The radially outer end of the second through hole 26d opens to the radially inner side of the bearing holding portion 11c on the other axial side of the bearing 71. The second through holes 26a to 26d are provided in plural numbers in the circumferential direction R, for example. The second through hole 26c may be open to the radial inner side of the bearing holding portion 13g in one axial direction of the bearing 70.

The rotor core 22 has, for example, an annular shape centered on the central axis J1. The rotor core 22 has a magnet insertion hole 22a penetrating the rotor core 22 in the axial direction Y. The magnet insertion holes 22a are provided in plurality in the circumferential direction R, for example. Magnets 23 are inserted into the plurality of magnet insertion holes 22a, respectively. The magnet 23 is bonded to the rotor core 22 with an adhesive or the like, for example. The method of fixing the magnet 23 is not limited to adhesion.

The first end plate 24 and the second end plate 25 have a circular ring plate shape expanding in the radial direction. The motor shaft 20a passes through the first end plate 24 and the second end plate 25. The first end plate 24 and the second end plate 25 sandwich the rotor core 22 in the axial direction Y in a state of being in contact with the rotor core 22. The first end plate 24 is disposed on one axial side of the rotor core 22. The first end plate 24 has an ejection slot, not shown. The second end plate 25 is disposed on the other axial side of the rotor core 22. The second end plate 25 has an ejection slot. The discharge grooves provided in the first end plate 24 and the second end plate 25 extend in the radial direction.

The first end plate 24, the rotor core 22, and the second end plate 25 are sandwiched in the axial direction Y by the nut 27 and the flange 21 f. The first end plate 24, the rotor core 22, and the second end plate 25 are pressed against the flange portion 21f by the nut 27 by screwing the nut 27 into the male screw portion provided on the outer peripheral surface of the motor shaft 20 a. Thereby, the first end plate 24, the rotor core 22, and the second end plate 25 are fixed to the motor shaft 20 a.

The stator 30 is radially opposed to the rotor 20 via a gap. The stator 30 has a stator core 31 and a plurality of coils 32 fitted to the stator core 31. The stator core 31 has an annular shape centered on the central axis J1. The radially outer side surface of the stator core 31 is fixed to the inner circumferential surface of the water jacket 60. The stator core 31 faces the radially outer side of the rotor core 22 with a gap therebetween.

In the present embodiment, the radially outer surface of the stator 30 corresponds to the radially outer surface of the stator core 31. The radially outer surface of the stator core 31 contacts the inner circumferential surface of the first tube 61 of the water jacket 60. More specifically, the stator core 31 is fixed to the water jacket 60 by press-fitting or shrink-fitting, for example.

The coil 32 is wound around the stator core 31. One axial end of the coil 32 is a coil end 32a that protrudes to one axial side from one axial end of the stator core 31. That is, the coil 32 has a coil end 32a protruding to one axial side of the stator core 31. The end of the coil 32 on the other axial side is a coil end 32b that protrudes to the other axial side than the end of the stator core 31 on the other axial side.

The conductive bus bar 101 and the bus bar holder 33 are disposed adjacent to the coil end 32 a. The bus bar 101 is held by the bus bar holder 33, and extends from a position adjacent to the coil end 32a to a position adjacent to the cable connection portion 102. The bus bar 101 connects an end of the coil 32 to one end of the bus bar 101, and connects the cable connection unit 102 to the other end of the bus bar 101, thereby allowing the coil 32 and the cable connection unit 102 to be electrically connected. The cable connection portion 102 is disposed in the wiring housing portion 11 e. Although not shown, the cable connection portion 102 is connected to the connector 100. Power is supplied to the connector 100 from a power supply not shown. Thereby, power is supplied from the connector 100 to the coil 32 via the cable connection portion 102 and the bus bar 101.

The rotation detecting unit 80 shown in fig. 2 detects rotation of the rotor 20. In the present embodiment, the rotation detecting unit 80 is, for example, a VR (Variable Reluctance) type resolver. The rotation detecting portion 80 is disposed radially inward of the outer cylinder portion 13 e. The rotation detecting unit 80 includes a detected unit 81 and a sensor unit 82. The detection target portion 81 has a ring shape extending in the circumferential direction R. The detection section 81 is fitted and fixed to the motor shaft 20 a. The detected part 81 is made of a magnetic substance.

The sensor portion 82 is disposed between the rotor core 22 and the cover portion 13 in the axial direction Y. The sensor unit 82 is annular and surrounds the detection unit 81 on the radially outer side. The sensor portion 82 has a plurality of coils in the circumferential direction R. When the detection section 81 is rotated together with the motor shaft 20a, an induced voltage corresponding to the circumferential position of the detection section 81 is generated in the coil of the sensor section 82. The sensor section 82 detects the rotation of the detected section 81 by detecting the induced voltage. Thereby, the rotation detecting unit 80 detects the rotation of the motor shaft 20a, and further, the rotation of the rotor 20.

The pump section 40 is provided in the center of the cover 13. The pump section 40 is disposed on one axial side of the motor shaft 20 a. The pump section 40 in the present embodiment is a so-called mechanical oil pump. The pump section 40 includes an external gear 42, an internal gear 43, the pump chamber 46, a suction port 44, a discharge port 45, and a reservoir section 48. The external gear 42 is a gear rotatable about the central axis J1. The external gear 42 is fixed to one axial end of the motor shaft 20 a. The external gear 42 is housed in the pump chamber 46. As shown in fig. 3, the external gear 42 has a plurality of teeth 42a on the outer peripheral surface. The tooth profile of the tooth portion 42a of the external gear 42 is a trochoid tooth profile.

The ring gear 43 is an annular gear rotatable about a rotation shaft J2 eccentric with respect to the center shaft J1. The internal gear 43 is housed in the pump chamber 46. The internal gear 43 surrounds the radially outer side of the external gear 42, and meshes with the external gear 42. The internal gear 43 has a plurality of teeth 43a on the inner peripheral surface. The tooth profile of the tooth portion 43a of the internal gear 43 is a trochoid tooth profile. In this way, the tooth profile of the tooth portion 42a of the external gear 42 and the tooth profile of the tooth portion 43a of the internal gear 43 are trochoid tooth profiles, and thus a trochoid pump can be configured. Therefore, noise generated by the pump unit 40 can be reduced, and the pressure and amount of the oil O discharged from the pump unit 40 can be easily stabilized.

In the present embodiment, after the internal gear 43 and the external gear 42 are inserted from the opening on one side in the axial direction of the recessed portion 13i, the opening on one side in the axial direction of the recessed portion 13i is closed by the plug portion 14, whereby the pump chamber 46 can be configured, and the internal gear 43 and the external gear 42 can be housed in the pump chamber 46. Therefore, the pump section 40 can be easily assembled.

As described above, the suction port 44 is connected to the first oil passage 13 a. As shown in fig. 6, the suction port 44 opens to the other side in the axial direction of the pump chamber 46. The suction port 44 is connected to a gap between the outer gear 42 and the inner gear 43. The suction port 44 can suck the oil O stored in the housing portion 17 from the opening portion 13h into the pump chamber 46, more specifically, into the gap between the external gear 42 and the internal gear 43, via the first oil passage 13 a. As shown in fig. 3, the suction port 44 is disposed above the lower end of the reservoir 48 and above the lower end of the external gear 42.

As described above, the discharge port 45 is connected to the second oil passage 20b via the connection oil passage 13 n. As shown in fig. 6, the discharge port 45 opens to one axial side of the pump chamber 46. The discharge port 45 is connected to the gap between the outer gear 42 and the inner gear 43. The discharge port 45 can discharge the oil O from the pump chamber 46, more specifically, from the gap between the external gear 42 and the internal gear 43.

The reservoir portion 48 is connected to the pump chamber 46 at one axial side of a vertically lower region of the pump chamber 46. As shown in fig. 3, the shape of the reservoir 48 is a bow shape that bulges downward when viewed in the axial direction. A part of the oil O sucked into the pump chamber 46 from the suction port 44 flows into the reservoir 48.

Since the suction port 44 is disposed above the lower end of the reservoir 48, at least a part of the oil O flowing into the reservoir 48 is stored in the reservoir 48 without returning from the suction port 44 to the storage 17 even when the pump 40 is stopped. Thus, when the pump section 40 is stopped, the lower portion of the external gear 42 and the lower portion of the internal gear 43 in the pump chamber 46 can be brought into contact with the oil O in the reservoir section 48. Therefore, after the pump section 40 is driven again, the oil O can be interposed between the tooth portions 42a of the external gear 42 and the tooth portions 43a of the internal gear 43 and between the inner circumferential surface of the pump chamber 46 and the outer circumferential surface of the internal gear 43, and the occurrence of seizure can be suppressed.

When the rotor 20 rotates and the motor shaft 20a rotates, the external gear 42 fixed to the motor shaft 20a rotates. Thereby, the internal gear 43 meshing with the external gear 42 rotates, and the oil O sucked into the pump chamber 46 from the suction port 44 is sent to the discharge port 45 through between the external gear 42 and the internal gear 43. Thus, the pump section 40 is driven via the motor shaft 20 a. The oil O discharged from the discharge port 45 flows into the connection oil passage 13n, and then flows into the second oil passage 20b from the connection port 13 p. As indicated by arrows in fig. 6, the oil O flowing into the second oil passage 20b is subjected to a radially outward force by the centrifugal force of the rotating motor shaft 20a, and flows out of the motor shaft 20a through the second through holes 26a to 26 d.

In the present embodiment, since the second through holes 26a and 26b are open to the gap between the first end plate 24 and the rotor core 22 and the gap between the second end plate 25 and the rotor core 22, the oil O flowing out of the second through holes 26a and 26b is discharged radially outward from the discharge grooves, not shown, provided in the respective end plates.

The oil O ejected radially outward from the ejection slot is blown to the coil 32. This enables the coil 32 to be cooled by the oil O. In the present embodiment, since the second oil passage 20b is provided inside the motor shaft 20a, the rotor 20 can be cooled by the oil O before being discharged from the discharge groove. In this way, the oil O discharged from the discharge port 45 in the present embodiment is guided to the rotor 20 and the stator 30.

Since the second through holes 26c and 26d are opened radially inward in the vicinity of the bearings 70 and 71, the oil O flowing out of the second through holes 26c and 26d is supplied to the bearings 70 and 71, respectively. This enables the oil O to be used as a lubricant for the bearings 70 and 71.

As described above, the pump section 40 can be driven by the rotation of the motor shaft 20a, and the oil O stored in the casing 10 can be pumped up by the pump section 40 and supplied to the rotor 20, the stator 30, and the bearings 70 and 71. That is, the pump unit 40 conveys the oil O stored in the storage unit 17 to at least one of the stator 30 and the rotor 20. This enables the rotor 20 and the stator 30 to be cooled by the oil O stored in the housing 10, and improves the lubricity between the bearings 70 and 71 and the motor shaft main body 21.

As described above, according to the present embodiment, the oil O discharged from the discharge port 45 can be fed to the inside of the motor shaft 20a by providing the connection oil passage 13n and the second oil passage 20 b. Since the second through holes 26a to 26d are provided, the oil O flowing into the second oil passage 20b can be supplied to the stator 30 and the bearings 70 and 71.

Further, according to the present embodiment, the second oil passage 20b provided in the motor shaft 20a opens to the connection oil passage 13n connected to the discharge port 45 at the end portion on one axial side of the motor shaft 20 a. Since the external gear 42 is fixed to the end portion on one axial side of the motor shaft 20a, the end portion on one axial side of the motor shaft 20a is disposed at a position closer to the discharge port 45. Therefore, the length of the connection oil passage 13n connecting the discharge port 45 and the second oil passage 20b can be shortened. As a result, according to the present embodiment, the entire length of the oil passage from the opening 13h to the second oil passage 20b can be easily shortened. This facilitates the supply of the oil O to the second oil passage 20b provided inside the motor shaft 20 a. Further, the structure of the motor 1 is easily simplified, and the motor 1 can be easily manufactured.

The oil O supplied to the stator 30 and the bearings 70 and 71 flows down in the housing 17 and is stored again in the lower region of the housing 17. This allows the pump unit 40 to circulate the oil O in the housing 17.

The motor 1 is further provided with a cooling flow path 90 through which a refrigerant flows. The cooling flow path 90 is provided in the cylindrical portion 10 a. That is, the cylindrical portion 10a that supports the stator 30 from the radially outer side has a cooling flow passage 90 through which the refrigerant flows. Here, as described above, the oil O is stored inside the housing portion 17 housing the stator 30. Therefore, the oil O stored in the housing 17 can be cooled by flowing the refrigerant to the cooling flow path 90 provided in the cylindrical portion 10 a. This allows the oil O to be cooled without being guided to the outside of the casing 10. As a result, it is not necessary to provide the casing 10 with an oil passage or the like for guiding the oil O to the outside of the casing 10, and the structure of the motor 1 can be prevented from becoming complicated. Further, since it is not necessary to lead the oil O to the outside of the casing 10, the casing 10 is easily sealed.

As described above, according to the present embodiment, the motor 1 capable of appropriately cooling the oil O stored in the casing 10 with a simple structure is obtained. Thus, as described above, by supplying the oil O to the stator 30, the rotor 20, and the like by the pump unit 40, the stator 30, the rotor 20, and the like can be appropriately cooled by the appropriately cooled oil O. The coolant flowing through the cooling channel 90 is not particularly limited as long as it is a fluid capable of cooling the oil O. The refrigerant may be water, a liquid other than water, or a gas.

Further, according to the present embodiment, the cooling passage 90 is provided in the cylindrical portion 10a that supports the stator 30 from the radially outer side. Therefore, the stator 30 can be directly cooled by the refrigerant flowing through the cooling passage 90. Further, since the oil O is stored in the casing 10, the rotor 20 is easily cooled by circulating the oil O in the casing 10. Further, as shown in fig. 2, since a part of the stator 30 can be immersed in the stored oil O, the stator 30 can be cooled more easily. In particular, since a part of the coil 32 as a heat generating body can be immersed in the stored oil O to be cooled, the stator 30 can be cooled appropriately.

In the present embodiment, the axial direction Y is orthogonal to the vertical direction Z. Therefore, for example, compared to the case where the axial direction Y is parallel to the vertical direction Z, the portion of the stator 30 immersed in the stored oil O is easily increased, and the stator 30 is easily cooled. Further, at least when the rotor 20 rotates, the liquid surface OS of the oil O is easily arranged below the rotor 20, and the oil O can be suppressed from becoming rotational resistance of the rotor 20 when the rotor 20 rotates.

Further, according to the present embodiment, the housing 10 has the fin portion 63 protruding into the housing portion 17. Therefore, the fin portion 63 can be brought into contact with the oil O stored in the housing portion 17. This can increase the contact area between the casing 10 and the oil O. As a result, the heat of the oil O is easily transferred to the casing 10 via the fin 63, and the oil O is easily cooled. In particular, in the present embodiment, since the cooling flow path 90 is provided in the cylindrical portion 10a of the casing 10, the heat transferred from the oil O to the casing 10 via the fin portion 63 is easily transferred to the refrigerant flowing through the cooling flow path 90. Therefore, the oil O can be cooled more efficiently.

Further, according to the present embodiment, the fin portion 63 is provided in the first tube portion 61 constituting the tube portion 10 a. Therefore, the heat moved to the casing 10 via the fin 63 is easily moved to the refrigerant flowing through the cooling flow path 90 provided in the cylinder 10 a. This enables the oil O to be cooled more efficiently via the fin 63.

Further, according to the present embodiment, the plurality of fin portions 63 are provided in the lower portion of the tube portion 10 a. Therefore, the fin 63 is easily disposed below the liquid surface OS of the oil O, and the fin 63 is easily brought into contact with the oil O. This enables the oil O to be cooled more appropriately via the fin 63.

Further, according to the present embodiment, the fin portion 63 protrudes toward the lid portion 13 to one side in the axial direction, and faces the lid portion 13 in the axial direction. Therefore, the oil O flowing toward the first oil passage 13a provided in the cover 13 in the housing 17 can be easily brought into contact with the fin portion 63. This enables the oil O flowing toward the first oil passage 13a to be appropriately cooled. As a result, the temperature of the oil O discharged into the casing 10 through the first oil passage 13a can be appropriately lowered, and the entire motor 1 can be efficiently cooled.

Further, according to the present embodiment, at least a part of the fin portion 63 faces the opening 13h of the first oil passage 13 a. Therefore, the oil O flowing toward the first oil passage 13a can be brought into contact with the fin portion 63 more appropriately. This enables the oil O flowing into the first oil passage 13a from the opening 13h to be cooled more efficiently. As a result, the temperature of the oil O discharged into the casing 10 through the first oil passage 13a can be appropriately lowered, and the entire motor 1 can be cooled more efficiently.

Further, according to the present embodiment, the fin 63 protrudes from the tube 10a to a position on one axial side of the coil end 32a of the stator 30. Therefore, the length of the fin portion 63 in the axial direction Y is easily increased, and the contact area between the fin portion 63 and the oil O is easily increased. This enables the heat of the oil O to be efficiently transferred to the casing 10.

Further, according to the present embodiment, the distance between the end portion on one side in the axial direction of the fin portion 63 in the axial direction Y and the cover 13 is shorter than the distance between the coil end portion 32a and the cover 13 in the axial direction Y. With this configuration, the length of the fin 63 in the axial direction Y can be easily increased, and the contact area between the fin 63 and the oil O can be easily increased. Therefore, the heat of the oil O can be efficiently transferred to the casing 10.

In the present embodiment, the cooling passage 90 is disposed between the first cylindrical portion 61 and the second cylindrical portion 11b in the radial direction. Therefore, the cooling flow path 90 can be easily configured by combining two cylindrical members. In the present embodiment, the cooling flow path 90 is configured by closing the opening on the outer circumferential surface of the first tube portion 61 on the radially outer side of the groove 61a by the flow path configuration portion 11d of the second tube portion 11 b.

As shown in fig. 7, the cooling flow path 90 extends in the circumferential direction R. Therefore, the cooling flow passage 90 easily surrounds the periphery of the stator 30, and the stator 30 can be cooled more appropriately by the refrigerant flowing through the cooling flow passage 90. In the present embodiment, the cooling flow path 90 extends in a wave shape in the circumferential direction R. This allows the refrigerant flowing through the cooling passage 90 to flow in the circumferential direction R while moving in the axial direction Y, thereby more appropriately cooling the stator 30 and the oil O. At least a part of the cooling channel 90 is located above the liquid surface OS of the oil O stored in the storage unit 17. Therefore, the portion of the stator 30 that is not immersed in the oil O in the housing 17 can be cooled by the refrigerant flowing through the cooling passage 90.

The cooling flow passage 90 includes a plurality of first flow passage portions 91a, 91b, 91c, 91d, 91e, and 91f extending in the axial direction Y and a plurality of second flow passage portions 92a, 92b, 92c, 92d, and 92e extending in the circumferential direction R of the stator 30. The plurality of first channel portions 91a to 91f are arranged in the circumferential direction R. The plurality of first channel portions 91a, 91b, 91c, 91d, 91e, and 91f are arranged in order from one circumferential side starting from the first channel portion 91a toward the other circumferential side. One axial end of the first flow path portion 91a is disposed on one axial side of the one axial end of the first flow path portions 91b to 91 f. The ends of the first flow path portions 91a to 91f on the other axial side are arranged at the same position in the axial direction Y.

The second channel portion 92a connects the end of the first channel portion 91a on the other axial side to the end of the first channel portion 91b on the other axial side. The second flow path portion 92b connects one axial end of the first flow path portion 91b to one axial end of the first flow path portion 91 c. The second channel portion 92c connects the end of the first channel portion 91c on the other axial side to the end of the first channel portion 91d on the other axial side. The second flow path portion 92d connects one axial end of the first flow path portion 91d to one axial end of the first flow path portion 91 e. The second channel portion 92e connects the end of the first channel portion 91e on the other axial side to the end of the first channel portion 91f on the other axial side.

As described above, the plurality of first channel portions 91a to 91f are connected to each other. Therefore, the coolant can be made to flow in the axial direction Y in the first flow path portions 91a to 91f, and the cooling flow path 90 can be configured in a wave shape. The plurality of second flow path portions 92a to 92e extend in the circumferential direction R along the radially outer side of the stator 30. This enables the stator 30 and the oil O to be cooled more appropriately by the refrigerant flowing through the cooling passage 90. Further, the directions of the refrigerant flowing inside between the first flow path portions 91a to 91f adjacent to each other in the circumferential direction R are opposite to each other.

As shown in fig. 2, the cooling flow path 90 overlaps the stator 30 and the rotor 20 when viewed in the vertical direction Z. When viewed in the vertical direction Z, an end portion on one axial side of the cooling flow passage 90 and an end portion on the other axial side of the cooling flow passage 90 overlap the stator core 31.

In the present embodiment, the cooling flow path 90 extends in the circumferential direction R on the radially outer side of the stator core 31 of the stator 30. Substantially the entire radial outer circumference of the stator core 31 is in contact with the water jacket 60. This enables stator core 31 to be cooled more efficiently by the coolant flowing through cooling flow path 90. Further, the cooling flow path 90 can be more easily manufactured than in the case where the cooling flow path is formed inside the stator core, for example.

As shown in fig. 7, the cooling channel 90 includes an inflow channel 93a and an outflow channel 93 b. The inflow channel 93a extends in the width direction X from the surface on the other side in the width direction of the second cylindrical portion 11b to the end on one side in the axial direction of the first channel portion 91 a. The opening on the other side in the width direction of the inflow channel 93a is an inflow port 93c into which the refrigerant flows. That is, the cooling channel 90 has an inlet 93 c. The inlet 93c is open on the other side surface in the width direction of the second tube 11 b. As shown in fig. 1, an inflow nozzle portion 15 protruding from the second tube portion 11b to the other side in the width direction is provided at the inflow port 93 c.

As shown in fig. 7, the outflow channel 93b extends in the width direction X from the surface on the other side in the width direction of the second cylindrical portion 11b to the end on the one side in the axial direction of the first channel portion 91 f. The opening on the other widthwise side of the outflow channel 93b is an outflow port 93d through which the refrigerant flows out. That is, the cooling channel 90 has an outlet 93 d. The outlet 93d opens on the other side surface in the width direction of the second tube 11 b. As shown in fig. 1, an outlet nozzle portion 16 is provided at the outlet 93d so as to project from the second tube portion 11b to the other side in the width direction.

As described above, the inlet 93c and the outlet 93d are open in the width direction X. Therefore, the inlet 93c and the outlet 93d can be more easily provided than in the case where the inlet and the outlet are opened in the axial direction Y or the vertical direction Z. In the present embodiment, since the inlet 93c and the outlet 93d are provided on the same side in the width direction X of the casing 10, the refrigerant can easily flow into the cooling channel 90 and flow out of the cooling channel 90. The inlet 93c and the outlet 93d are arranged in the vertical direction Z. The inflow port 93c is located above the outflow port 93 d. The vertical position of the inlet 93c and the vertical position of the outlet 93d may be the same.

The refrigerant flowing from the inflow nozzle portion 15 into the inflow channel 93a through the inflow port 93c passes through the first channel portions 91a, the first channel portions and the second channel portions in this order, and then flows into the outflow channel 93b from the first channel portion 91 f. The refrigerant having flowed into the outflow channel 93b then flows out of the outflow nozzle portion 16 to the outside of the cooling channel 90 through the outflow port 93 d. In this way, the refrigerant circulates in the cooling flow path 90.

The motor 1 of the present embodiment described above is mounted on, for example, a drive device 2 shown in fig. 8. The drive device 2 is mounted on a vehicle and rotates wheels of the vehicle. The drive device 2 includes a motor 1, a reduction gear 3, a differential gear 4, and a gear box 6. The gear case 6 internally houses the reduction gear 3 and the differential gear 4. The gear box 6 is fixed to a housing 10 of the motor 1. The oil O is stored inside the gear case 6.

The reduction gear 3 is connected to the motor 1. The reduction gear 3 is connected to an output shaft portion 21b of the motor shaft 20 a. The reduction gear 3 reduces the rotation speed of the motor 1, and increases the torque output from the motor 1 according to the reduction ratio. The reduction gear 3 transmits the torque output from the motor 1 to the differential device 4. The reduction gear 3 has a first gear 3a, a second gear 3b, a third gear 3c, and an intermediate shaft 3 d.

The first gear 3a is fixed to the outer peripheral surface of the output shaft portion 21 b. The intermediate shaft 3d is disposed at a position radially outward from the intermediate shaft J1 and extends in the axial direction Y. The second gear 3b and the third gear 3c are fixed to the outer peripheral surface of the intermediate shaft 3 d. The second gear 3b and the third gear 3c are connected via an intermediate shaft 3 d. The second gear 3b and the third gear 3c rotate about the central axis of the intermediate shaft 3 d. The second gear 3b meshes with the first gear 3 a. The third gear 3c meshes with a below-described ring gear 4a of the differential device 4.

The torque output from the electric motor 1 is transmitted to the differential device 4 via the reduction gear 3. More specifically, the torque output from the electric motor 1 is transmitted to the ring gear 4a of the differential device 4 via the motor shaft 20a, the first gear 3a, the second gear 3b, the intermediate shaft 3d, and the third gear 3c in this order. The gear ratio of each gear, the number of gears, and the like can be variously changed according to a required reduction ratio. In the present embodiment, the reduction gear 3 is a parallel-axis gear type reduction gear in which the axes of the gears are arranged in parallel.

The differential device 4 is connected to the reduction gear 3. Thereby, the differential device 4 is connected to the motor 1 via the reduction gear 3. The differential device 4 is a device that transmits the torque output from the motor 1 to the wheels of the vehicle. When the vehicle turns, the differential device 4 absorbs a speed difference between the left and right wheels and transmits the same torque to the axles 5 of the left and right wheels. Thereby, the differential device 4 rotates the axle 5.

The differential device 4 includes a ring gear 4a, a gear box not shown, a pair of pinion gears not shown, a pinion shaft not shown, and a pair of side gears not shown. The ring gear 4a meshes with the third gear 3 c. Thereby, the torque output from the motor 1 is transmitted to the ring gear 4a via the reduction gear 3. The lower end of the ring gear 4a is immersed in the oil O stored in the gear case 6. Thereby, the ring gear 4a is rotated to lift the oil O. The raised oil O is supplied to the reduction gear 3 and the differential device 4 as, for example, lubricating oil.

The present invention is not limited to the above embodiment, and other configurations may be adopted. The number of fin units is not particularly limited as long as it is one or more. The fin part is arranged on the shell. For example, the fin portion may be provided in the second tube portion, or may be provided in both the first tube portion and the second tube portion. The fin portion may be provided at an upper portion of the tube portion. The fin portion may be provided in a portion other than the tube portion. In this case, for example, the fin portion may be provided on the cover portion 13 or the bottom portion 11a of the above-described embodiment. The shape of the fin portion is not particularly limited. The fin portion may be cylindrical or polygonal. The plurality of fin portions may have different shapes. The plurality of fin portions may include fin portions having different projecting directions.

The shape of the cooling flow path 90 is not particularly limited. The cooling flow path 90 may not have a wave shape, and may be a wide flow path extending linearly in the width direction X, or a wide flow path extending linearly in the axial direction Y, for example. A plurality of cooling channels 90 may be provided. The first channel portions 91a to 91f may have the same size and the same shape in their channel cross sections. The cooling flow path 90 may have a uniform flow path cross-sectional area as a whole or may have a locally different flow path cross-sectional area.

The inlet 93c and the outlet 93d may be open on the opposite side to each other in the width direction X. The inlet 93c and the outlet 93d may be provided on one of the body and the water jacket of the case so as to be separated from the other of the body and the water jacket. That is, for example, the inlet 93c and the outlet 93d may be provided in the body of the case so as to be separated from the water jacket. In this case, the inlet 93c and the outlet 93d may be provided in the body portion other than the second tube portion.

In the above-described embodiment, the cooling flow path 90 is configured by providing the groove 61a on the outer peripheral surface of the water jacket 60, but the present invention is not limited thereto. For example, a groove may be provided on the inner peripheral surface of the second tube 11b, and the cooling flow path may be configured by closing the groove with the outer peripheral surface of the water jacket 60. In this case, the outer peripheral surface of the water jacket 60 may be provided with no groove or a groove facing a groove provided in the inner peripheral surface of the second tube 11 b. The member constituting the cooling flow path may be in contact with the stator core.

One direction in which the center axis extends, that is, the axial direction in which the motor shaft 20a extends is not particularly limited, and may be orthogonal to the vertical direction Z, or may be parallel to the vertical direction Z. The rotor core 22 may be fixed to the outer peripheral surface of the motor shaft main body 21 by press fitting or the like. In this case, the first end plate 24 and the second end plate 25 may not be provided. In this case, the oil O flowing out of the second through holes 26a and 26b may be directly supplied to the coils 32, or holes connected to the second through holes 26a and 26b may be provided in the rotor core 22, and the oil O may be supplied to the coils 32 through the holes of the rotor core 22. The oil O discharged from the motor shaft 20a may be supplied to the stator core 31.

The location of supplying the oil O discharged from the discharge port 45 is not particularly limited, and may be supplied to only one or two of the rotor 20, the stator 30, and the bearings 70 and 71, or may not be supplied to any one of them, for example. The oil O discharged from the discharge port 45 may be supplied to, for example, the inner surface of the vertically upper region of the housing 17. In this case, the stator 30 can be indirectly cooled by cooling the housing 10. Further, any one or more of the second through holes 26a to 26d may not be provided. The tooth profile of the tooth portion 42a of the external gear 42 and the tooth profile of the tooth portion 43a of the internal gear 43 may be cycloid tooth profiles or involute tooth profiles. The pump unit 40 may be configured to deliver the oil O to either the stator 30 or the rotor 20. The pump section 40 may not be provided.

The use of the motor of the above embodiment is not particularly limited. The motor according to the above embodiment is mounted on a vehicle, for example. Further, the present invention may be used not as a motor but as a generator. Further, the above-described structures can be appropriately combined within a range not inconsistent with each other.

Description of the symbols

1-motor, 10-housing, 10 a-tube, 11 b-second tube, 13-cover, 13 a-first oil path, 13 h-opening, 17-housing, 20-rotor, 20 a-motor shaft, 20 b-second oil path, 26a, 26b, 26c, 26 d-second through hole (through hole), 30-stator, 31-stator core, 32-coil, 32a, 32 b-coil end, 40-pump section, 45-discharge port, 46-pump chamber, 61-first tube, 63-fin, 90-cooling flow path, J1-center axis, O-oil, R-circumferential, Y-axial, Z-vertical direction.

Claims (10)

1. A motor is characterized by comprising:

a rotor having a motor shaft disposed along a central axis extending in one direction;

a stator that faces the rotor in a radial direction with a gap interposed therebetween; and

a housing having a housing portion for housing the rotor and the stator and capable of storing oil,

the housing has a cylindrical portion for supporting the stator from a radially outer side,

the cylinder part has a cooling flow path for flowing a refrigerant,

the housing has a fin portion protruding into the housing.

2. The motor of claim 1,

the tube portion includes:

a cylindrical first cylindrical portion supporting the stator from a radially outer side; and

a cylindrical second cylindrical portion located radially outward of the first cylindrical portion,

the cooling flow path is disposed between the first cylindrical portion and the second cylindrical portion in the radial direction.

3. The motor of claim 2,

the fin portion is provided on at least one of the first tube portion and the second tube portion.

4. The motor according to any one of claims 1 to 3,

the fin portion is provided at a vertically lower portion of the cylinder portion.

5. The motor according to any one of claims 1 to 4,

includes a pump section driven via the motor shaft,

the pump section includes:

a pump chamber;

a suction port capable of sucking oil from the housing into the pump chamber; and

a discharge port capable of discharging oil from the pump chamber,

the housing has a lid portion for closing one end portion of the cylindrical portion in the axial direction,

the cover has a first oil passage connecting the inside of the housing with the suction port,

the motor shaft includes:

a second oil passage provided inside the motor shaft and connected to the discharge port; and

a through hole connecting the second oil passage to the outer peripheral surface of the motor shaft,

the fin portion protrudes in one axial direction toward the cover portion and is axially opposed to the cover portion.

6. The motor of claim 5,

the first oil passage has an opening portion that opens into the housing portion,

at least a part of the fin portion faces the opening.

7. The motor according to any one of claims 1 to 6,

the stator has a stator core and a coil mounted to the stator core,

the coil has a coil end portion protruding to one side in the axial direction of the stator core,

the fin portion protrudes from the tube portion to one side in the axial direction with respect to the coil end portion.

8. The motor according to any one of claims 1 to 7,

the cooling flow path extends in the circumferential direction.

9. The motor of claim 8,

the cooling flow path extends in a wave shape in the circumferential direction.

10. The motor according to claim 8 or 9,

at least a part of the cooling flow path is positioned above an oil level of oil stored in the storage unit in a vertical direction.

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