JP7764166B2 - Rotor and rotating electric machine - Google Patents

Description

The present invention relates to a rotor and a rotating electric machine.

A rotating electric machine includes a rotor that can rotate around a central axis and a stator located radially outward of the rotor. The rotor has multiple rotor core sections aligned in the axial direction. Patent Document 1 discloses a rotor in which multiple core blocks are circumferentially offset by a predetermined skew angle and overlap in the axial direction.

Patent No. 6688327

In conventional rotors, the relative positions of the magnetic poles and through holes are consistent in each rotor core (core block). As a result, the opening positions of the through holes are misaligned at the boundaries between rotor cores. For example, when the through holes are used as refrigerant flow paths, this can increase resistance at the boundaries of the rotor cores, potentially hindering the smooth flow of refrigerant.

One of the objectives of the present invention is to provide a rotor and a rotating electric machine that can suppress misalignment between through holes.

A rotor according to one embodiment of the present invention is a rotor for a rotating electric machine that rotates about a central axis. The rotor includes a first rotor portion and a second rotor portion that are circumferentially offset from each other and stacked in the axial direction. The first rotor portion includes a first rotor core having a first through hole extending axially, and a first magnet held by the first rotor core. The second rotor portion includes a second rotor core having a second through hole extending axially, and a second magnet held by the second rotor core. The magnetic poles of the first rotor portion are offset circumferentially to one side relative to the magnetic poles of the second rotor portion. In the first rotor portion, the center of the first through hole is offset circumferentially to the other side by a first angle from the magnetic poles of the first rotor portion. In the second rotor portion, the center of the second through hole is offset circumferentially to the other side by a second angle from the magnetic poles of the second rotor portion. The second angle is greater than the first angle. At the boundary between the first rotor section and the second rotor section, the opening of the first through hole and the opening of the second through hole overlap each other when viewed in the axial direction.

The present invention provides a rotor and a rotating electrical machine that can suppress misalignment between through holes.

FIG. 1 is a schematic diagram of a drive device according to an embodiment. FIG. 2 is a perspective view of a rotor according to one embodiment. FIG. 3 is a cross-sectional perspective view of a rotor according to one embodiment. FIG. 4 is a plan view of the first rotor portion of one embodiment. FIG. 5 is a plan view of the second rotor portion of one embodiment. FIG. 6 is a schematic cross-sectional view of a rotor according to an embodiment taken along the axial direction. FIG. 7 is a schematic cross-sectional view of a rotor according to an embodiment. FIG. 8 is a schematic diagram of a flow path configuration of a rotor that can be employed in one embodiment. FIG. 9 is a schematic cross-sectional view of a rotor according to the first modification. FIG. 10 is a schematic cross-sectional view of a rotor according to the second modification. FIG. 11 is a schematic cross-sectional view of a rotor according to the third modification. FIG. 12 is a plan view of a rotor according to the fourth modification. FIG. 13 is a plan view of a rotor according to the fifth modification. FIG. 14 is a schematic cross-sectional view of a rotor according to the sixth modification. FIG. 15 is a schematic cross-sectional view of a rotor according to the seventh modification.

In the following explanation, the vertical direction is defined based on the positional relationship when the drive unit of the embodiment is mounted on a vehicle positioned on a horizontal road surface. In other words, the relative positional relationship in the vertical direction described in the following embodiments only needs to be satisfied when the drive unit is mounted on a vehicle positioned on a horizontal road surface.

In the drawings, the XYZ coordinate system is shown as a three-dimensional Cartesian coordinate system where appropriate. In the XYZ coordinate system, the Z axis direction is the vertical direction. The +Z side is the upper vertical side, and the -Z side is the lower vertical side. In the following description, the upper vertical side will simply be referred to as the "upper side," and the lower vertical side will simply be referred to as the "lower side." The X axis direction is perpendicular to the Z axis direction and corresponds to the fore-and-aft direction of the vehicle on which the drive unit is mounted. In the following embodiments, the +X side is the front side of the vehicle, and the -X side is the rear side of the vehicle. The Y axis direction is perpendicular to both the X axis direction and the Z axis direction and corresponds to the left-right direction of the vehicle, i.e., the vehicle width direction. In the following embodiments, the +Y side is the left side of the vehicle, and the -Y side is the right side of the vehicle. The fore-and-aft direction and the left-and-right direction are horizontal directions perpendicular to the vertical direction.

Note that the positional relationship in the front-to-rear direction is not limited to that in the following embodiments; the +X side may be the rear of the vehicle and the -X side may be the front of the vehicle. In this case, the +Y side is the right side of the vehicle and the -Y side is the left side of the vehicle. Also, in this specification, "parallel direction" includes a direction that is approximately parallel, and "orthogonal direction" includes a direction that is approximately orthogonal.

The central axis J, shown in the appropriate figures, is an imaginary axis extending in a direction intersecting the vertical direction. More specifically, the central axis J extends in the Y-axis direction, which is perpendicular to the vertical direction, i.e., in the left-right direction of the vehicle. In the following description, unless otherwise specified, the direction parallel to the central axis J will be referred to simply as the "axial direction," the radial direction centered on the central axis J will be referred to simply as the "radial direction," and the circumferential direction centered on the central axis J, i.e., around the axis of the central axis J, will be referred to simply as the "circumferential direction." In this embodiment, one axial side corresponds to the right side (-Y side), and the other axial side corresponds to the left side (+Y side).

The arrow θ shown in the figures indicates the circumferential direction. In the following description, the side of the circumferential direction that moves clockwise around the central axis J when viewed from the right side, i.e., the side toward which the arrow θ points (+θ side), will be referred to as "one circumferential side," and the side of the circumferential direction that moves counterclockwise around the central axis J when viewed from the right side, i.e., the side opposite to the side toward which the arrow θ points (-θ side), will be referred to as "the other circumferential side."

FIG. 1 is a schematic diagram of a driving device 100 according to this embodiment.
The drive unit 100 is mounted on a vehicle and rotates an axle 64. The vehicle on which the drive unit 100 is mounted is a vehicle powered by a motor, such as a hybrid electric vehicle (HEV), a plug-in hybrid electric vehicle (PHV), or an electric vehicle (EV). As shown in FIG. 1 , the drive unit 100 includes a rotating electric machine 10, a housing 80, a transmission device 60, and a refrigerant flow path 90. The rotating electric machine 10 includes a rotor 30 that rotates about a central axis J, and a stator 40 that surrounds the rotor 30 from the radially outer side. Other configurations of the rotating electric machine 10 will be described later.

The housing 80 houses the rotating electric machine 10 and the transmission device 60. The housing 80 has a motor housing 81 and a gear housing 82. The motor housing 81 houses the rotor 30 and the stator 40 inside. 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, for example, separate from the peripheral wall portion 81a and the partition wall portion 81b.

The peripheral wall portion 81a is cylindrical and surrounds the central axis J, opening to the right. The partition portion 81b is connected to the left end of the peripheral wall portion 81a. The partition portion 81b axially separates the interior of the motor housing 81 from the interior of the gear housing 82. The partition portion 81b has a partition opening 81d that connects the interior of the motor housing 81 with the interior of the gear housing 82. The partition portion 81b holds the bearing 34. 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. The lid portion 81c holds the bearing 35.

The gear housing 82 houses the reduction gear 62 and differential gear 63 (described later) of the transmission device 60, as well as refrigerant O. The refrigerant O is stored in a lower region within the gear housing 82. The refrigerant O circulates within a refrigerant flow path 90 (described later). The refrigerant O is used to cool the rotating electrical machine 10. The refrigerant O is preferably oil that lubricates the reduction gear 62 and differential gear 63. For example, it is preferable to use, as the refrigerant O, an oil equivalent to a relatively low-viscosity automatic transmission lubricant (ATF: Automatic Transmission Fluid), in order to perform the functions of both refrigerant and lubricant.

The transmission device 60 is connected to the rotating electric machine 10 and transmits the rotation of the rotor 30 to an axle 64 of the vehicle. The transmission device 60 of this 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 device 63 has a ring gear 63a. Torque output from the rotating electric machine 10 is transmitted to the ring gear 63a via the reduction device 62. A lower end of the ring gear 63a is immersed in the refrigerant O stored in the gear housing 82. As the ring gear 63a rotates, the refrigerant O is scooped up. The scooped up refrigerant O is supplied to the reduction device 62 and the differential device 63, for example, as lubricating oil.

The rotating electric machine 10 is the part that drives the drive unit 100. The rotating electric machine 10 is located, for example, to the right of the transmission device 60. In this embodiment, the rotating electric machine 10 is a motor. The torque of the rotor 30 of the rotating electric machine 10 is transmitted to the transmission device 60.

The rotor 30 comprises a shaft 31 extending axially around the central axis J, eight rotor sections 20 fixed to the shaft 31, at least one spacer 38 arranged between axially adjacent rotor sections 20, and a pair of end plates 39 arranged at both axial ends of the stacked rotor sections 20.

The shaft 31 extends axially around the central axis J. The shaft 31 rotates around the central axis J. The shaft 31 is rotatably supported by bearings 34 and 35. In this embodiment, the shaft 31 is a hollow shaft having a hollow portion 31h extending axially. The shaft 31 is cylindrical, through which refrigerant O can flow. The shaft 31 extends across the interior of the motor housing 81 and the interior of the gear housing 82. The left end of the shaft 31 protrudes into the interior of the gear housing 82. The reduction gear 62 is connected to the left end of the shaft 31.

Fig. 2 is a perspective view of the rotor 30 of this embodiment. Fig. 3 is a cross-sectional perspective view of the rotor 30 of this embodiment.
As shown in FIG. 3 , the shaft 31 is substantially cylindrical. The inner diameter of the end of the shaft 31 on one axial side (−Y side) is smaller than the inner diameter of the remaining portion of the shaft 31 on that side. The shaft 31 has a portion where the inner diameter gradually or stepwise increases from the end on that side toward the other axial side (+Y side). This portion corresponds to the upstream portion of a shaft flow path portion 95 of a refrigerant flow path 90, which will be described later. The shaft 31 is provided with a refrigerant guide portion 31a recessed radially outward from the inner circumferential surface of the shaft 31, and a refrigerant supply hole (communication hole) 33 penetrating the circumferential wall of the shaft 31.

The refrigerant guide portion 31a is an annular groove centered on the central axis J. The refrigerant guide portion 31a has a pair of groove walls 31b, 31c spaced apart in the axial direction, and a groove bottom 31d located between the pair of groove walls 31b, 31c in the axial direction and facing radially inward. Of the pair of groove walls 31b, 31c, one groove wall 31b located on one axial side is tapered radially outward toward the other axial side. Therefore, the refrigerant O flowing from one axial side to the other axial side within the shaft 31 is stably guided to the groove bottom 31d by one groove wall 31b. Of the pair of groove walls 31b, 31c, the other groove wall 31c located on the other axial side is flat and extends in a direction perpendicular to the central axis J, facing toward one axial side. This prevents the refrigerant O guided to the groove bottom 31d from climbing over the other groove wall 31c to the other axial direction, ensuring that the refrigerant O is stably held in the refrigerant guide portion 31a. The groove bottom 31d is located at the radially outermost position in the refrigerant guide portion 31a.

The refrigerant supply hole 33 is a circular hole extending radially inside the peripheral wall of the shaft 31. That is, the refrigerant supply hole 33 extends radially outward from the hollow portion 31h. Multiple refrigerant supply holes 33 are provided in the shaft 31. The multiple refrigerant supply holes 33 are arranged at intervals in the circumferential direction. In this embodiment, eight refrigerant supply holes 33 are provided at equal intervals in the circumferential direction. The refrigerant supply holes 33 open to the groove bottom 31d. That is, the refrigerant supply holes 33 open to the refrigerant guide portion 31a. According to this embodiment, the refrigerant O flowing inside the shaft 31 is efficiently guided to the refrigerant supply hole 33 by the refrigerant guide portion 31a, and flows through the rotor 30 as described below, thereby improving the cooling efficiency of the rotor 30.

As shown in Figure 3, each of the multiple rotor sections 20 has a rotor core 26 and magnets 27, 28, and 29. In the following description, when comparing rotor sections 20 stacked in the axial direction, one will be referred to as the first rotor section 20A and the other as the second rotor section 20B.

FIG. 4 is a plan view of the first rotor portion 20A, and FIG. 5 is a plan view of the second rotor portion 20B.
The rotor core 26 and magnets 27, 28, and 29 of the first rotor section 20A are referred to as the first rotor core 26A and first magnets 27A, 28A, and 29A, respectively. The rotor core 26 and magnets 27, 28, and 29 of the second rotor section 20B are referred to as the second rotor core 26B and second magnets 27B , 28B, and 29B, respectively. That is, the rotor 30 includes the first rotor section 20A and the second rotor section 20B, which are stacked in the axial direction. The first rotor section 20A includes the first rotor core 26A and the first magnets 27A, 28A, and 29A. The second rotor section 20B includes the second rotor core 26B and the second magnets 27B, 28B, and 29B.

The rotor core 26 is made of a magnetic material. The rotor core 26 is cylindrical and centered on the central axis J, and in this embodiment is cylindrical. The inner circumferential surface of the rotor core 26 is fixed to the outer circumferential surface of the shaft 31 by press fitting or the like. The rotor core 26 and the shaft 31 are fixed so that they cannot move relative to each other in the axial, radial, or circumferential directions. The rotor core 26 has multiple electromagnetic steel plates (not shown) stacked in the axial direction.

Each rotor core 26 has multiple (eight in this embodiment) through holes 21 and multiple (24 in this embodiment) magnet accommodating holes 22, 23, 24. The through holes 21 and magnet accommodating holes 22, 23, 24 of the first rotor core 26A are referred to as first through holes 21A and first magnet accommodating holes 22A, 23A, 24A, respectively. The through holes 21 and magnet accommodating holes 22, 23, 24 of the second rotor core 26B are referred to as second through holes 21B and second magnet accommodating holes 22B, 23B, 24B, respectively.

First magnets 27A, 28A, and 29A are inserted into the first magnet accommodating holes 22A, 23A, and 24A, respectively. Second magnets 27B, 28B, and 29B are inserted into the second magnet accommodating holes 22B, 23B, and 24B, respectively.

The magnet accommodating holes 22, 23, and 24 penetrate the rotor core 26 in the axial direction. When viewed from the axial direction, the magnet accommodating holes 22, 23, and 24 are generally square-shaped, and in this embodiment, generally rectangular. Magnets 27, 28, and 29 are accommodated in the magnet accommodating holes 22, 23, and 24, respectively. The multiple magnet accommodating holes 22, 23, and 24 include sets of three magnet accommodating holes 22, 23, and 24 that are laid out in the shape of an isosceles triangle when viewed from the axial direction.

Of the three magnet accommodating holes 22, 23, and 24 that make up one set, the radial positions of the two circumferentially aligned magnet accommodating holes 23 and 24 overlap with the radial position of the through hole 21. In other words, the through hole 21 and the magnet accommodating holes 23 and 24 are arranged side by side in the circumferential direction.

The through holes 21 pass through the rotor core 26 in the axial direction. In this embodiment, the through holes 21 are circular when viewed in the axial direction. However, the shape of the through holes 21 is not limited to this embodiment, and the through holes 21 may have other shapes, such as a substantially rectangular shape when viewed in the axial direction.

A plurality of through holes 21 are provided in the rotor core 26 at intervals in the circumferential direction. In this embodiment, eight through holes 21 are provided in each rotor core 26 at equal intervals in the circumferential direction. Each through hole 21 is disposed between circumferentially adjacent magnet accommodating holes 23, 24. The configuration of the through holes 21 will be described in more detail later.

As shown in FIG. 2, in the rotor 30 of this embodiment, four rotor sections 20 are provided on each of the axial sides of the spacer 38. At least two of the multiple rotor sections 20 are arranged with their circumferential positions offset from one another. In other words, in this embodiment, a step skew is provided in the rotor 30, which reduces cogging torque and torque ripple, suppresses vibration of the rotating electric machine 10, and improves rotational efficiency.

In the rotor 30, the multiple rotor sections 20 stacked on one axial side (-Y side) of the spacer 38 are shifted to one circumferential side (+θ side) as they move away from the spacer 38 to one axial side (-Y side).

In the rotor 30, the multiple rotor sections 20 stacked on the other axial side (+Y side) of the spacer 38 are shifted to one circumferential side (+θ side) as they move away from the spacer 38 toward the other axial side (+Y side).

The direction of the step skew twist of the multiple rotor sections 20 arranged on one axial side of the spacer 38 is different from the direction of the step skew twist of the multiple rotor sections 20 arranged on the other axial side of the spacer 38. This has the effect of further reducing cogging torque and torque ripple.

Magnets 27, 28, 29 are, for example, neodymium magnets or ferrite magnets. Magnets 27, 28, 29 are, for example, rectangular plate-shaped. As shown in Figures 4 and 5, multiple magnets 27, 28, 29 are provided in rotor section 20. Each magnet 27, 28, 29 is housed in a corresponding magnet housing hole 22, 23, 24.

Magnets 27, 28, and 29 are fixed to the rotor section 20, for example, with an adhesive (not shown). The three magnets 27, 28, and 29, housed in the three magnet housing holes 22, 23, and 24 and laid out in an isosceles triangle, form one magnetic pole 25.

In this embodiment, the rotor section 20 is provided with eight magnetic poles 25. The eight magnetic poles 25 are, for example, arranged at equal intervals around the circumference. A through hole 21 is disposed between adjacent magnetic poles 25 in the circumferential direction.

The multiple magnetic poles 25 are classified into magnetic poles 25 that form north poles on the outer peripheral surface of the rotor section 20 and magnetic poles 25 that form south poles on the outer peripheral surface of the rotor section 20. The magnetic poles 25 that form north poles and the magnetic poles 25 that form south poles are arranged alternately in the circumferential direction. The configuration of each magnetic pole 25 is similar except that the north/south orientation on the outer peripheral surface of the rotor section 20 is different and the circumferential position is different.

The three magnets 27, 28, 29 that make up one magnetic pole 25 are classified into one outer magnet 27 and a pair of inner magnets 28, 29. The outer magnet 27 is positioned at the base of an isosceles triangle when viewed axially. The outer magnet 27 is positioned at the radially outer end of the isosceles triangle and extends circumferentially. The pair of inner magnets 28, 29 are positioned at the two equal sides (equal sides) of the isosceles triangle when viewed axially. The pair of inner magnets 28, 29 are positioned radially inward of the outer magnet 27. One of the pair of inner magnets 28, 29, located on the other circumferential side (-θ side), is positioned radially inward as it moves toward one circumferential side (+θ side). The other of the pair of inner magnets 28, 29, located on one circumferential side (+θ side), is positioned radially outward as it moves toward one circumferential side (+θ side).

In this embodiment, the magnetic pole 25 is composed of three magnets 27, 28, and 29, and each of the magnets 27, 28, and 29 is arranged in the shape of an isosceles triangle. However, the magnetic pole may be composed of one or more magnets arranged in various shapes, as long as the multiple magnetic poles have the same configuration.

Next, the relative arrangement of the first rotor section 20A and the second rotor section 20B, which are stacked adjacent to each other, will be described with reference to FIGS.
Here, the description will be focused on one magnetic pole 25 and the through-hole 21 arranged on the other circumferential side (-θ side) of the magnetic pole 25 in the first rotor portion 20A and the second rotor portion 20B. However, the other magnetic poles 25 and the other through-holes 21 have the same configuration.

In the following description, the magnetic pole 25 of the first rotor portion 20A will be referred to as the first magnetic pole 25A, and the magnetic pole 25 of the second rotor portion 20B will be referred to as the second magnetic pole 25B. In addition, when viewed from the axial direction, an imaginary line passing through the central axis J and the circumferential center of the first magnetic pole 25A will be referred to as the first magnetic pole center line L1, and an imaginary line passing through the central axis J and the circumferential center of the second magnetic pole 25B will be referred to as the second magnetic pole center line L2.
Note that the first magnetic pole center line L1 and the second magnetic pole center line L2 can be provided in the same number as the number of magnetic poles 25 in each rotor 30, but here we will focus on only one magnetic pole center line L1, L2 for each rotor 30.

The rotor 30 of this embodiment has a step skew. That is, the first rotor section 20A and the second rotor section 20B are arranged with a circumferential offset from each other and stacked in the axial direction. Therefore, the magnetic poles 25 of the first rotor section 20A are arranged with a circumferential offset to one side (+θ side) relative to the magnetic poles 25 of the second rotor section 20B. Here, the angle of the circumferential offset between the first rotor section 20A and the second rotor section 20B is referred to as the skew angle φ. The skew angle φ is the angle between the first magnetic pole center line L1 and the second magnetic pole center line L2.

As shown in FIG. 4, when viewing the first rotor portion 20A from the axial direction, an imaginary line passing through the central axis J and the center of the first through hole 21A is referred to as the first through hole center line P1. The first through hole center line P1 is located on the other circumferential side (-θ side) of the first magnetic pole center line L1. The first through hole center line P1 and the first magnetic pole center line L1 form a first angle α1. In other words, in the first rotor portion 20A, the center of the first through hole 21A is located at a position offset by the first angle α1 to the other circumferential side (-θ side) from the magnetic pole 25 (first magnetic pole 25A) of the first rotor portion 20A.

As shown in FIG. 5, when viewing the second rotor portion 20B from the axial direction, an imaginary line passing through the central axis J and the center of the second through hole 21B is referred to as the second through hole center line P2. The second through hole center line P2 is located on the other circumferential side (-θ side) of the second magnetic pole center line L2. The second through hole center line P2 and the second magnetic pole center line L2 form a second angle α2. In other words, in the second rotor portion 20B, the center of the second through hole 21B is located at a position offset by the second angle α2 to the other circumferential side (-θ side) from the magnetic pole 25 (second magnetic pole 25B) of the second rotor portion 20B.

In this embodiment, the second angle α2 is greater than the first angle α1. Therefore, the first through holes 21A and the second through holes 21B can be offset in a direction that offsets the circumferential misalignment between the first rotor portion 20A and the second rotor portion 20B toward one side (+θ) in the circumferential direction due to step skew of the rotor 30. This reduces the circumferential misalignment between the through holes 21 at the boundaries of each rotor portion 20. This embodiment makes it easier to arrange the through holes 21 of multiple rotor portions 20 in a linear alignment in the axial direction. For example, when multiple axially connected through holes 21 are used as a flow path for refrigerant O, the increase in pipeline resistance at the boundaries between the rotor portions 20 can be suppressed, allowing the refrigerant O to flow smoothly.

In this embodiment, either the first angle α1 or the second angle α2 may be 0°. However, to clarify the magnitude relationship between the first angle α1 and the second angle α2, the first angle α1 and the second angle α2 must be positive angles. That is, the first angle α1 and the second angle α2 are each angles greater than or equal to 0°. Note that when the first angle α1 is 0°, the first magnetic pole center line L1 and the first through hole center line P1 overlap. When the second angle α2 is 0°, the second magnetic pole center line L2 and the second through hole center line P2 overlap.

FIG. 6 is a schematic cross-sectional view of the rotor 30 of this embodiment taken along the axial direction.
The multiple rotor portions 20 are fixed to the outer peripheral surface of the shaft 31. That is, the first rotor portion 20A and the second rotor portion 20B are fixed to the outer peripheral surface of the shaft 31. The first rotor portion 20A and the second rotor portion 20B face each other and contact each other at a boundary portion 32.

According to this embodiment, the opening 21Aa of the first through hole 21A and the opening 21Ba of the second through hole 21B overlap each other when viewed from the axial direction at the boundary 32 between the first rotor portion 20A and the second rotor portion 20B. According to this embodiment, the internal space of the first through hole 21A and the internal space of the second through hole 21B can be made to communicate with each other at the boundary 32.

4 and 5, in this embodiment, the difference between the first angle α1 and the second angle α2 (α2-α1) corresponds to the skew angle φ between the first rotor section 20A and the second rotor section 20B. That is, in this embodiment, the first angle α1, the second angle α2, and the skew angle φ satisfy the following formula:
φ=α2-α1

By satisfying the above formula, the rotor 30 of this embodiment has the first through-hole center line P1 and the second through-hole center line P2 aligned with each other when viewed axially. This makes it easier to arrange the first through-hole 21A and the second through-hole 21B in a straight line.

In this embodiment, the distance between the first through hole 21A and the central axis J is equal to the distance between the second through hole 21B and the central axis J. Therefore, in this embodiment, the centers of the first through hole 21A and the second through hole 21B coincide with each other when viewed in the axial direction. This allows the first through hole 21A and the second through hole 21B to be arranged linearly along the axial direction, preventing a step from occurring between the first through hole 21A and the second through hole 21B at the boundary between the rotor sections 20.

In addition, in this embodiment, the first through hole 21A and the second through hole 21B have the same shape when viewed axially. Therefore, at the boundary between the first rotor portion 20A and the second rotor portion 20B, the opening 21Aa of the first through hole 21A and the opening 21Ba of the second through hole 21B are aligned with each other when viewed axially. As a result, no step is formed between the first through hole 21A and the second through hole 21B at the boundary between the rotor portions 20. When the through holes 21 are used as refrigerant flow paths, an increase in conduit resistance at the boundary between the first through hole 21A and the second through hole 21B can be suppressed. Furthermore, when assembling the rotor 30 by stacking the first rotor portion 20A and the second rotor portion 20B, the first rotor portion 20A and the second rotor portion 20B may be aligned circumferentially using a jig that penetrates the first through hole 21A and the second through hole 21B.

As shown in FIG. 3, the spacer 38 is a non-magnetic ring-shaped plate centered on the central axis J, and in this embodiment is an annular plate. The axial dimension, i.e., the plate thickness, of the spacer 38 is greater than the plate thickness of each of the multiple electromagnetic steel plates in the rotor section 20.

The spacer 38 has a spacer flow passage portion 96. The spacer flow passage portion 96 is recessed radially outward from the inner circumferential surface of the spacer 38. The spacer flow passage portion 96 opens to the inner circumferential surface of the spacer 38 but not to the outer circumferential surface. The spacer flow passage portion 96 connects the refrigerant supply hole 33 and the through-hole 21. The hollow portion 31h of the shaft 31 is connected to the through-holes 21 (i.e., the first through-hole 21A and the second through-hole 21B) via the refrigerant supply hole 33. According to this embodiment, the refrigerant O flowing through the shaft 31 is supplied from the refrigerant supply hole 33 through the spacer flow passage portion 96 to the through-holes 21 of the rotor core 26 by centrifugal force or the like. The rotor 30 is cooled by the refrigerant O flowing through the through-hole 21. Because the temperature rise of the rotor 30 can be suppressed, the range of materials for the rotor 30 can be expanded, for example, by using inexpensive magnets 27, 28, and 29 whose upper limit of operating temperature is not too high. Furthermore, unlike, for example, the electromagnetic steel plates that make up the rotor core 26, the spacer 38 of this embodiment can be freely changed in thickness and shape of the spacer flow path portion 96, and design changes are easy; in other words, there is a high degree of freedom in shape, so it can easily meet the requirements for various rotating electric machines 10.

The spacer flow passage portion 96 penetrates the spacer 38 in the axial direction. In this case, while the spacer 38 has a simple configuration, the refrigerant O can be supplied from the spacer flow passage portion 96 to the through-holes 21 of the rotor core 26 located on one axial side of the spacer 38 and the through-holes 21 of the rotor core 26 located on the other axial side of the spacer 38, thereby cooling the rotor 30 evenly over a wide area in the axial direction. Multiple spacer flow passage portions 96 are provided on the spacer 38 at intervals from one another in the circumferential direction. In this embodiment, eight spacer flow passage portions 96 are provided on the spacer 38 at equal intervals in the circumferential direction.

The end plates 39 are ring-shaped and centered on the central axis J, and in this embodiment, are annular. A pair of end plates 39 are provided at both axial ends of a laminate formed by multiple rotor sections 20. The pair of end plates 39 axially contact the rotor cores 26 located at one axial end and the other axial end of the multiple rotor cores 26. The end plates 39 face the rotor cores 26 from the axial side opposite the spacer 38.

The end plate 39 has a guide passage portion 97 that communicates with the through hole 21. The guide passage portion 97 has a circumferential passage portion 97a, a radial passage portion 97b, and a communicating passage portion 97c. The circumferential passage portion 97a is recessed axially from the surface of the end plate 39 that faces the rotor core 26 in the axial direction and is groove-shaped that extends circumferentially. The circumferential passage portion 97a is annular and centered on the central axis J. The circumferential passage portion 97a faces the through hole 21 in the axial direction. The circumferential passage portion 97a communicates with multiple through holes 21 lined up circumferentially in the rotor core 26 that faces the end plate 39.

The radial flow passages 97b are grooves recessed in the axial direction from the surface of the end plate 39 facing away from the rotor core 26 in the axial direction and extending radially. The radial flow passages 97b open to the outer peripheral surface of the end plate 39. In other words, the radial flow passages 97b open radially outward. Multiple radial flow passages 97b are provided circumferentially and spaced apart from one another. The number of radial flow passages 97b is, for example, the same as the number of through holes 21 in the rotor core 26 facing the end plate 39, and is eight in this embodiment.

The communicating flow passage portion 97c is a hole that penetrates the end plate 39 in the axial direction. The communicating flow passage portion 97c communicates between the circumferential flow passage portion 97a and the radial flow passage portion 97b. In this embodiment, the communicating flow passage portion 97c opens to a radially outer end portion of the circumferential flow passage portion 97a and a radially inner end portion of the radial flow passage portion 97b. A plurality of communicating flow passage portions 97c are provided at intervals from one another in the circumferential direction.
The number of communication flow passage portions 97c is the same as the number of radial flow passage portions 97b, and in this embodiment, for example, is eight.

The guide flow passage portion 97 guides the refrigerant O that flows into the guide flow passage portion 97 from the through-hole 21 toward the coil 42c (described later) of the stator 40 (see Figure 1). According to this embodiment, the refrigerant O that has flowed through the through-hole 21 and cooled the rotor 30 can be used to further cool the coil 42c, thereby improving cooling efficiency.

As shown in FIG. 1, the stator 40 faces the rotor 30 in the radial direction with a gap between them. The stator 40 surrounds the rotor 30 from the radial outside along the entire circumferential direction. The stator 40 is fixed inside the motor housing 81. The stator 40 has a stator core 41 and a coil assembly 42.

The stator core 41 is annular and surrounds the central axis J of the rotating electric machine 10. The stator core 41 is constructed by stacking multiple plate members, such as electromagnetic steel sheets, in the axial direction. The coil assembly 42 has multiple coils 42c attached to the stator core 41 along the circumferential direction. The multiple coils 42c are attached to each tooth (not shown) of the stator core 41 via insulators (not shown). The multiple coils 42c are arranged along the circumferential direction. The coils 42c have portions that protrude axially from the stator core 41.

The refrigerant flow path 90 is provided within the housing 80. Refrigerant O flows through the refrigerant flow path 90. The refrigerant flow path 90 spans the interior of the motor housing 81 and the interior of the gear housing 82. The refrigerant flow path 90 is a path through which the refrigerant O stored in the gear housing 82 is supplied to the rotating electric machine 10 in the motor housing 81 and then returns to the gear housing 82. The refrigerant flow path 90 is provided with a pump 71 and a cooler 72. The refrigerant flow path 90 has a first flow path section 91, a second flow path section 92, a third flow path section 93, a stator refrigerant supply section 50, a shaft flow path section 95, a connection flow path section 94, a spacer flow path section 96, a through-hole flow path section 98, and a guide flow path section 97.

The first flow path portion 91, the second flow path portion 92, and the third flow path portion 93 are provided, for example, in the wall portion of the gear housing 82. The first flow path portion 91 connects the pump 71 to the portion of the interior of the gear housing 82 where the refrigerant O is stored. The second flow path portion 92 connects the pump 71 to the cooler 72. The third flow path portion 93 connects the cooler 72 to the stator refrigerant supply portion 50. In this embodiment, the third flow path portion 93 is connected to the left end of the stator refrigerant supply portion 50, i.e., the upstream portion of the stator refrigerant supply portion 50.

The stator refrigerant supply unit 50 supplies refrigerant O to the stator 40. In this embodiment, the stator refrigerant supply unit 50 is tubular and extends axially. In other words, in this embodiment, the stator refrigerant supply unit 50 is a pipe extending axially. Both axial ends of the stator refrigerant supply unit 50 are supported by the motor housing 81. The left end of the stator refrigerant supply unit 50 is supported, for example, by the partition wall portion 81b. The right end of the stator refrigerant supply unit 50 is supported, for example, by the lid portion 81c. The stator refrigerant supply unit 50 is located radially outside the stator 40. In this embodiment, the stator refrigerant supply unit 50 is located above the stator 40.

The stator refrigerant supply unit 50 has a supply port 50a that supplies the refrigerant O to the stator 40. In this embodiment, the supply port 50a is an injection port that injects a portion of the refrigerant O that has flowed into the stator refrigerant supply unit 50 to the outside of the stator refrigerant supply unit 50. The supply port 50a is configured as a hole that penetrates the wall of the stator refrigerant supply unit 50 from the inner peripheral surface to the outer peripheral surface.
A plurality of supply ports 50a are provided in the stator coolant supply portion 50. The plurality of supply ports 50a are arranged, for example, at intervals from one another in the axial or circumferential direction.

As shown in FIG. 3, the shaft flow passage portion 95 is disposed in the hollow portion 31h within the shaft 31. The shaft flow passage portion 95 includes the inner circumferential surface of the shaft 31, the refrigerant guide portion 31a, and the refrigerant supply hole 33. As shown in FIG. 1, the connection flow passage portion 94 connects the interior of the stator refrigerant supply portion 50 to the interior of the shaft 31. The connection flow passage portion 94 connects the right end, i.e., the downstream portion, of the stator refrigerant supply portion 50 to the right end, i.e., the upstream portion, of the shaft flow passage portion 95. The connection flow passage portion 94 is provided, for example, in the lid portion 81c. According to this embodiment, the configuration of the refrigerant flow passage 90 can be simplified while stably cooling the stator 40 and rotor 30.

The through-hole flow passage portion 98 connects the spacer flow passage portion 96 and the guide flow passage portion 97. The through-hole flow passage portion 98 is arranged throughout the interiors of multiple rotor cores 26.

As shown in FIG. 1, when the pump 71 is driven, the refrigerant O stored in the gear housing 82 is sucked up through the first flow path portion 91 and flows into the cooler 72 through the second flow path portion 92. The refrigerant O that flows into the cooler 72 is cooled within the cooler 72 and then flows through the third flow path portion 93 to the stator refrigerant supply portion 50. A portion of the refrigerant O that flows into the stator refrigerant supply portion 50 is sprayed from the supply port 50a and supplied to the stator 40. Another portion of the refrigerant O that flows into the stator refrigerant supply portion 50 flows through the connection flow path portion 94 into the shaft flow path portion 95. A portion of the refrigerant O flowing through the shaft flow path portion 95 flows from the refrigerant supply hole 33 through the spacer flow path portion 96, the through-hole flow path portion 98, and the guide flow path portion 97, and is scattered onto the stator 40. Another portion of the refrigerant O that flows into the shaft flow path 95 is discharged into the gear housing 82 from the opening on the left side of the shaft 31 and is again stored within the gear housing 82.

The refrigerant O supplied to the stator 40 from the supply port 50a removes heat from the stator 40, and the refrigerant O supplied to the rotor 30 and stator 40 from within the shaft 31 removes heat from the rotor 30 and stator 40. After cooling the stator 40 and rotor 30, the refrigerant O falls downward and accumulates in the lower region of the motor housing 81. The refrigerant O that accumulates in the lower region of the motor housing 81 returns to the gear housing 82 through the partition opening 81d provided in the partition portion 81b. In this way, the refrigerant flow path 90 supplies the refrigerant O stored in the gear housing 82 to the rotor 30 and stator 40.

As shown in FIG. 1, the rotor 30 of this embodiment has a flow path (spacer flow path portion 96) that connects the entire axial length of the rotor 30 to the through-holes 21 of each rotor portion 20. As an alternative structure, as shown in FIG. 8, the rotor 30 may have a flow path 97A that connects from one or the other axial end of the rotor 30 to the through-hole 21 (i.e., the first through-hole 21A or the second through-hole 21B). The rotor 30 of this embodiment extends horizontally and is centered on the central axis J. However, the rotor 30 may also be centered on a central axis that extends vertically. In this case, a configuration can be adopted in which refrigerant O is introduced into the through-holes 21 of the rotor 30 by, for example, dripping refrigerant O from above.

Figure 7 is a schematic cross-sectional view of the rotor 30 of this embodiment, showing the positional relationship between the first through hole 21A and the second through hole 21B and the magnet. In this embodiment, the positional relationship between the first magnetic pole 25A and the first through hole 21A is different from the positional relationship between the second magnetic pole 25B and the second through hole 21B.

In the first rotor section 20A, the first distance between the first through hole 21A and the magnet 29 closest to the first through hole 21A is defined as d1. Similarly, in the second rotor section 20B, the second distance between the second through hole 21B and the magnet 29 closest to the second through hole 21B is defined as d2. In this embodiment, the second distance d2 is smaller than the first distance d1. Thus, according to this embodiment, a configuration is adopted in which the distance between the through hole 21 and the magnet 29 differs for each rotor section 20.

<Modification>
Hereinafter, various modifications that can be adopted in the above-described embodiment will be described.
In each of the modified examples, the circumferential positional relationship between the first through holes and the second through holes is the same as in the above-described embodiment. The rotor of each modified example differs from the rotor of the above-described embodiment in the shape of either or both of the first through holes and the second through holes.
In each of the modifications described below, the same components as those in the embodiment or modification already described are given the same reference numerals, and the description thereof will be omitted.

(Variation 1)
FIG. 9 is a schematic cross-sectional view of a rotor 130 according to the first modification.
In this modification, first through-holes 121A of first rotor portion 120A are tapered so that the diameter decreases toward boundary 132 with second rotor portion 120B (i.e., one axial side (-Y side)). When refrigerant O flows from first through-holes 121A to second through-holes 121B, the flow rate of refrigerant O passing through first through-holes 121A increases toward second through-holes 121B.

At the boundary 132 between the first rotor section 120A and the second rotor section 120B, the opening 121Aa of the first through hole 121A and the opening 121Ba of the second through hole 121B are aligned when viewed in the axial direction. Therefore, no step is created between the first through hole 121A and the second through hole 121B at the boundary 132 between the rotor sections 120, preventing an increase in pipeline resistance at the boundary 132.

(Variation 2)
FIG. 10 is a schematic cross-sectional view of a rotor 230 according to the second modification.
In this modification, the cross-sectional area of the first through hole 221A is smaller than the cross-sectional area of the second through hole 221B. The first through hole 221A and the second through hole 221B are, for example, circular when viewed in the axial direction. The diameter of the first through hole 221A is smaller than the diameter of the second through hole 221B.

At the boundary 232 between the first rotor section 220A and the second rotor section 220B, the opening 221Aa of the first through hole 221A is encompassed by the opening 221Ba of the second through hole 221B when viewed in the axial direction. Therefore, when refrigerant O flows from the first through hole 221A to the second through hole 221B, no step surface opposing the flow of refrigerant O is created at the boundary 232. This modification makes it possible to suppress an increase in pipeline resistance at the boundary 232.

(Variation 3)
FIG. 11 is a schematic cross-sectional view of a rotor 330 according to the third modification.
In this modification, the number of first through holes 321A provided in the first rotor portion 320A is greater than the number of second through holes provided in the second rotor portion 320B. The cross-sectional area of each first through hole 321A is smaller than the cross-sectional area of each second through hole 321B. The first through holes 321A and the second through holes 321B are, for example, circular when viewed in the axial direction. The diameter of each first through hole 321A is smaller than the diameter of each second through hole 321B.

At the boundary 332 between the first rotor section 320A and the second rotor section 320B, the openings 321Aa of the multiple (three) first through holes 321A are encompassed by the opening 321Ba of one second through hole 321B when viewed in the axial direction. Therefore, when refrigerant O flows from the first through hole 321A to the second through hole 321B, no step faces opposing the flow of refrigerant O are created at the boundary 332. This modification makes it possible to suppress an increase in pipeline resistance at the boundary 332.

(Variation 4)
FIG. 12 is a plan view of a rotor 430 of the fourth modified example, showing the first through-holes 421A of the first rotor portion 420A and the second through-holes 421B of the second rotor portion 420B.

At the boundary between the first rotor portion 420A and the second rotor portion 420B, the opening shapes of the first through hole 421A and the second through hole 421B are different from each other. The first through hole 421A is generally rectangular when viewed in the axial direction. On the other hand, the second through hole 421B is circular when viewed in the axial direction. Note that "approximately rectangular" here refers to a rectangular shape with smoothly curved corners. The cross-sectional shapes of the first through hole 421A and the second through hole 421B are uniform over their entire axial length. The centers of the first through hole 421A and the second through hole 421B are aligned when viewed in the axial direction. The cross-sectional area of the first through hole 421A is smaller than the cross-sectional area of the second through hole 421B.

When viewed from the axial direction, the first through hole 421A is encompassed by the second through hole 421B. That is, at the boundary between the first rotor portion 420A and the second rotor portion 420B, the opening of the first through hole 421A is encompassed by the opening of the second through hole 421B when viewed from the axial direction. Therefore, when refrigerant O flows from the first through hole 421A to the second through hole 421B, no step faces opposing the flow of refrigerant O are created at the boundary. According to this modification, even if the shapes of the first through hole 421A and the second through hole 421B are different from each other, an increase in pipe resistance at the boundary can be suppressed.

(Variation 5)
FIG. 13 is a plan view of a rotor 530 of the fifth modified example, showing a first through-hole 521A of a first rotor portion 520A and a second through-hole 521B of a second rotor portion 520B.

At the boundary between the first rotor portion 520A and the second rotor portion 520B, the opening shapes of the first through holes 521A and the second through holes 521B are different from each other. The first through holes 521A are substantially rectangular when viewed in the axial direction. On the other hand, the second through holes 521B are circular when viewed in the axial direction. The cross-sectional shapes of the first through holes 521A and the second through holes 521B are uniform over their entire axial lengths. The centers of the first through holes 521A and the second through holes 521B coincide with each other when viewed in the axial direction. The cross-sectional area of the first through holes 521A is smaller than the cross-sectional area of the second through holes 521B.

When viewed in the axial direction, the first through hole 521A overlaps the second through hole 521B. When viewed in the axial direction, a portion of the outer shape of the first through hole 521A extends outward relative to the outer shape of the second through hole 521B. Furthermore, a portion of the outer shape of the second through hole 521B extends outward relative to the outer shape of the first through hole 521A. According to this modification, a step is created at the boundary between the first through hole 521A and the second through hole 521B. Therefore, in the rotor 530 of this modification, although some turbulence occurs in the refrigerant O at the boundary between the first through hole 521A and the second through hole 521B, the center of the first through hole 521A and the center of the second through hole 521B coincide, allowing the refrigerant O to flow smoothly. According to this modification, even when the shapes of the first through hole 521A and the second through hole 521B are different from each other, an increase in pipe resistance at the boundary can be suppressed.

(Variation 6)
FIG. 14 is a schematic cross-sectional view of a rotor 630 according to the sixth modification.
In this modification, first through-holes 621A of first rotor portion 620A are tapered so that their diameters decrease toward boundary 632 with second rotor portion 620B. Similarly, second through-holes 621B of second rotor portion 620B are tapered so that their diameters decrease away from boundary 632 with first rotor portion 620A. Therefore, the cross-sectional areas of first through-holes 621A and second through-holes 621B, which are connected along the axial direction, decrease from the other axial side (+Y side) to one axial side (−Y side). When refrigerant O flows from first through-holes 621A to second through-holes 621B, the flow velocity of refrigerant O passing through first through-holes 621A and second through-holes 621B increases toward one axial side (−Y side).

At the boundary 632 between the first rotor section 620A and the second rotor section 620B, the opening 621Aa of the first through hole 621A and the opening 621Ba of the second through hole 621B are aligned when viewed in the axial direction. This prevents a step from occurring between the first through hole 621A and the second through hole 621B at the boundary 632 between the rotor sections 620, preventing an increase in pipeline resistance at the boundary 632.

In the first rotor section 620A, the first distance between the first through hole 621A and the magnet 29 closest to the first through hole 621A is defined as d1. Similarly, in the second rotor section 620B, the second distance between the second through hole 621B and the magnet 29 closest to the second through hole 621B is defined as d2. As in the above embodiment, the second distance d2 is smaller than the first distance d1.

As described above, in the rotor 630 of this modified example, the flow path cross-sectional area gradually decreases from the first through-hole 621A to the second through-hole 621B. As a result, the flow velocity of the refrigerant O passing through the first rotor portion 620A is lower than the flow velocity of the refrigerant O passing through the second rotor portion 620B. The refrigerant O passing through the interior of the rotor 630 of this modified example is in contact with the first rotor portion 620A for a longer period of time than with the second rotor portion 620B. The refrigerant O absorbs more heat from the first rotor portion 620A than from the second rotor portion 620B.

On the other hand, in rotor 630 of this modified example, second distance d2 is shorter than first distance d1. Therefore, in second rotor portion 620B, magnets 29 can be more easily cooled by refrigerant O than in first rotor portion 620A. According to this modified example, the flow rate of refrigerant O can be reduced in first rotor portion 620A , where magnets 29 are farther away from first through-holes 621A , and the flow rate of refrigerant O can be increased in second rotor portion 620B, where magnets 29 are closer to second through-holes 621B. This improves the balance of the cooling efficiency of each magnet 29 in first rotor portion 620A and second rotor portion 620B, allowing the entire rotor 630 to be cooled uniformly and suppressing temperature variations.

(Variation 7)
FIG. 15 is a schematic cross-sectional view of a rotor 730 according to the seventh modification.
In this modification, the axial dimension D1 of the first rotor portion 720A is larger than the axial dimension D2 of the second rotor portion 720B. The first through-hole 721A of the first rotor portion 720A and the second through-hole 721B of the second rotor portion 720B have the same shape when viewed in the axial direction. At a boundary 732 between the first rotor portion 720A and the second rotor portion 720B, the opening 721Aa of the first through-hole 721A and the opening 721Ba of the second through-hole 721B are aligned with each other when viewed in the axial direction.

In the first rotor section 720A, the first distance between the first through hole 721A and the magnet 29 closest to the first through hole 721A is defined as d1. Similarly, in the second rotor section 720B, the second distance between the second through hole 721B and the magnet 29 closest to the second through hole 721B is defined as d2. As in the above embodiment, the second distance d2 is smaller than the first distance d1.

In the rotor 730 of this modified example, the overall length of the first through hole 721A (i.e., axial dimension D1) is longer than the overall length of the second through hole 721B (i.e., axial dimension D2). Refrigerant O passing through the interior of the rotor 730 of this modified example is in contact with the first rotor portion 720A for a longer period of time than with the second rotor portion 720B. As a result, the refrigerant O absorbs more heat from the first rotor portion 720A than from the second rotor portion 720B.

On the other hand, in the rotor 730 of this modified example, the second distance d2 is shorter than the first distance d1. Therefore, in the second rotor portion 720B, it is easier to cool the magnets 29 with the refrigerant O than in the first rotor portion 720A. According to this modified example, the flow path length of the refrigerant O can be increased in the first rotor portion 720A , where the distance between the magnets 29 and the first through holes 721A is large, and the flow path length of the refrigerant O can be decreased in the second rotor portion 720B, where the distance between the magnets 29 and the second through holes 721B is small. This improves the balance of the cooling efficiency of the magnets 29 in the first rotor portion 720A and the second rotor portion 720B, allowing the entire rotor 730 to be cooled uniformly and suppressing temperature variations.

The above describes various embodiments of the present invention and their variations. However, the configurations and combinations thereof in each embodiment and variation are merely examples, and additions, omissions, substitutions, and other modifications to the configurations are possible without departing from the spirit of the present invention. Furthermore, the present invention is not limited to the embodiments and variations.

The rotating electric machine to which the present invention is applicable is not limited to a motor, but may also be a generator. The use of the rotating electric machine is not particularly limited. For example, the rotating electric machine may be mounted on a vehicle for an application other than rotating an axle, or may be mounted on equipment other than a vehicle. The attitude in which the rotating electric machine is used is not particularly limited.

10... rotating electric machine, 20, 120, 620... rotor portion, 20A, 120A, 220A, 320A, 420A, 520A, 620A, 720A... first rotor portion, 20B, 120B, 220B, 320B, 420B, 520B, 620B, 720B... second rotor portion, 21... through hole, 21A, 121A, 221A, 321A, 421A, 521 A, 621A, 721A...first through hole, 21Aa, 21Ba, 121Aa, 121Ba, 221Aa, 221Ba, 321Aa, 321Ba, 621Aa, 621Ba , 721Aa, 721Ba...Opening, 21B, 121B, 221B, 321B, 421B, 521B, 621B, 721B...Second through hole, 22, 23, 24...Magnet housing Holes, 22A, 23A, 24A...first magnet accommodating holes, 22B, 23B, 24B...second magnet accommodating holes, 25...magnetic poles, 25A...first magnetic poles, 25B...second magnetic poles, 26...rotor cores, 26A...first rotor cores, 26B...second rotor cores, 27, 28, 29...magnets, 27A, 28A, 29A...first magnets, 27B, 28B, 2 9B...second magnet; 30, 130, 230, 330, 430, 530, 630, 730...rotor; 31...shaft; 31h...hollow portion; 32, 132, 232, 332, 632, 732...boundary portion; 33...refrigerant supply hole (communication hole); 40...stator; 97A...flow path; J...center axis; α1...first angle; α2...second angle; φ...skew angle

Claims (9)

A rotor for a rotating electric machine that rotates about a central axis,
a first rotor portion and a second rotor portion that are circumferentially offset from each other and stacked in an axial direction;
The first rotor portion is
a first rotor core provided with a first through hole extending in the axial direction;
a first magnet held by the first rotor core,
The second rotor portion is
a second rotor core provided with a second through hole extending in the axial direction;
a second magnet held by the second rotor core,
the magnetic poles of the first rotor portion are arranged to be shifted to one side in the circumferential direction relative to the magnetic poles of the second rotor portion,
In the first rotor portion, a center of the first through hole is disposed at a position shifted by a first angle toward the other circumferential side from the magnetic pole of the first rotor portion,
In the second rotor portion, the center of the second through hole is disposed at a position shifted by a second angle toward the other circumferential side from the magnetic pole of the second rotor portion,
the second angle is greater than the first angle;
an opening of the first through hole and an opening of the second through hole overlap each other when viewed from the axial direction at a boundary between the first rotor portion and the second rotor portion;
the first through hole and the second through hole are refrigerant flow paths through which a refrigerant can flow,
At a boundary between the first rotor portion and the second rotor portion, an opening of the first through hole is included in an opening of the second through hole when viewed in the axial direction.
Rotor. A rotor for a rotating electric machine that rotates about a central axis,
a first rotor portion and a second rotor portion that are circumferentially offset from each other and stacked in an axial direction;
The first rotor portion is
a first rotor core provided with a first through hole extending in the axial direction;
a first magnet held by the first rotor core,
The second rotor portion is
a second rotor core provided with a second through hole extending in the axial direction;
a second magnet held by the second rotor core,
the magnetic poles of the first rotor portion are arranged to be shifted to one side in the circumferential direction relative to the magnetic poles of the second rotor portion,
In the first rotor portion, a center of the first through hole is disposed at a position shifted by a first angle toward the other circumferential side from the magnetic pole of the first rotor portion,
In the second rotor portion, the center of the second through hole is disposed at a position shifted by a second angle toward the other circumferential side from the magnetic pole of the second rotor portion,
the second angle is greater than the first angle;
an opening of the first through hole and an opening of the second through hole overlap each other when viewed from the axial direction at a boundary between the first rotor portion and the second rotor portion;
the first through hole and the second through hole are refrigerant flow paths through which a refrigerant can flow,
A hollow shaft having a central axis line as its center,
the first rotor portion and the second rotor portion are fixed to an outer circumferential surface of the shaft,
The shaft is provided with a communication hole extending radially outward from the hollow portion,
the hollow portion of the shaft is connected to the first through hole and the second through hole via the communication hole;
Rotor. A rotor for a rotating electric machine that rotates about a central axis,
a first rotor portion and a second rotor portion that are circumferentially offset from each other and stacked in an axial direction;
The first rotor portion is
a first rotor core provided with a first through hole extending in the axial direction;
a first magnet held by the first rotor core,
The second rotor portion is
a second rotor core provided with a second through hole extending in the axial direction;
a second magnet held by the second rotor core,
the magnetic poles of the first rotor portion are arranged to be shifted to one side in the circumferential direction relative to the magnetic poles of the second rotor portion,
In the first rotor portion, a center of the first through hole is disposed at a position shifted by a first angle toward the other circumferential side from the magnetic pole of the first rotor portion,
In the second rotor portion, a center of the second through hole is disposed at a position shifted by a second angle toward the other circumferential side from the magnetic pole of the second rotor portion,
the second angle is greater than the first angle;
an opening of the first through hole and an opening of the second through hole overlap each other when viewed from the axial direction at a boundary between the first rotor portion and the second rotor portion;
the first through hole and the second through hole are refrigerant flow paths through which a refrigerant can flow,
a flow path that connects from an end portion on one side or the other side of the rotor in the axial direction to the first through hole or the second through hole;
Rotor. a difference between the first angle and the second angle corresponds to a skew angle between the first rotor portion and the second rotor portion;
The rotor according to any one of claims 1 to 3 . an opening of the first through hole and an opening of the second through hole coincide with each other when viewed from the axial direction at a boundary between the first rotor portion and the second rotor portion;
A rotor according to claim 2 or 3 . The first rotor core is provided with a plurality of the first through holes,
At a boundary between the first rotor portion and the second rotor portion, openings of the plurality of first through holes are encompassed by an opening of one of the second through holes as viewed in the axial direction.
The rotor of claim 1 . an opening shape of the first through hole and an opening shape of the second through hole are different from each other at a boundary between the first rotor portion and the second rotor portion;
The rotor of claim 1 . the first rotor core is provided with a first magnet accommodating hole into which the first magnet is inserted,
the second rotor core is provided with a second magnet accommodating hole into which the second magnet is inserted,
The first through hole and the first magnet accommodating hole are arranged side by side in the circumferential direction,
The second through hole and the second magnet accommodating hole are arranged side by side in the circumferential direction.
A rotor according to any one of claims 1 to 7 . A rotor according to any one of claims 1 to 8 ;
a stator surrounding the rotor from the radially outer side,
Rotating electric motor.