JP2020018116A - Rotor and rotary electric machine - Google Patents

Abstract

To provide a rotor and a rotary electric machine, capable of effectively supplying a refrigerant to a desired place.SOLUTION: A rotor 4 includes: a shaft 31 extending along an axis C; and a rotor core 32 fixed to the shaft 31. On an inner peripheral surface of the shaft 31, a first spiral groove 91, extending spirally along the axis C, for guiding a refrigerant toward a rotor core 32 and a second spiral groove 92, extending spirally along the axis C, for guiding the refrigerant toward a second bearing 42 are formed.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a rotor and rotating electricity.

  In a rotating electric machine, when a current is supplied to a coil, a magnetic field is formed in a stator core, and magnetic attraction and repulsion are generated between a permanent magnet of the rotor and the stator core. Thereby, the rotor rotates with respect to the stator.

  With the above-described rotating electricity, the rotor generates heat due to the influence of eddy current generated in the magnet during rotation. If the magnetic force is reduced by heat generated by the magnet (so-called thermal demagnetization), the performance of the rotating electric machine may be reduced.

  Here, for example, Patent Document 1 below discloses a configuration in which a spiral groove is formed on an outer peripheral surface of a shaft to which a rotor core is fixed. According to this configuration, the refrigerant supplied from the first side end of the shaft flows through the spiral groove to the second side end, and then is folded back at the second side end to the first side end. Return. Thereby, the contact area between the rotor and the refrigerant (spiral groove) is increased.

JP-T-2015-534803A

  However, there is still room for improvement in the above-described prior art in that the refrigerant is effectively supplied to a desired location.

  An object of the present invention is to provide a rotor and rotary electricity capable of effectively supplying a refrigerant to a desired place.

(1) In order to achieve the above object, a rotor (for example, the rotor 4 in the embodiment) according to one embodiment of the present invention includes a shaft extending along an axis (for example, the shaft 31 in the embodiment) and a shaft. A fixed rotor core (for example, the rotor core 32 in the embodiment), and a first flow path that spirally extends along the axis on the peripheral surface of the shaft and guides the refrigerant toward the rotor core. (For example, a first spiral groove 91 in the embodiment) and a helical extending along the axis and guiding the refrigerant toward a portion different from the rotor core (for example, the second bearing 42 in the embodiment). Two flow paths (for example, the second spiral groove 92 in the embodiment) are formed.

(2) In the rotor according to the aspect of (1), the shaft is formed in a cylindrical shape, and the first flow path and the second flow path are formed on an inner peripheral surface of the shaft. Communicates with the first flow path, communicates with the first discharge port (for example, the first discharge port 62 in the embodiment) that opens on the outer peripheral surface of the shaft, and the second flow path, A second discharge port (for example, the second discharge port 63 in the embodiment) that opens on the outer peripheral surface of the shaft may be formed.

(3) In the rotor according to the aspect of (1) or (2), the first flow path and the second flow path may extend in parallel.

(4) In the rotor according to any one of the above aspects (1) to (3), the first flow path and the second flow path are different in at least one of a width in an axial direction and a depth in a radial direction. May be.

(5) The rotor according to any one of the above aspects (1) to (4), further including a shaft support portion (for example, the second bearing 42 in the embodiment) that supports the shaft so as to be rotatable around an axis. The second flow path may guide the refrigerant to the shaft support.

(6) A rotating electric machine according to one aspect of the present invention includes the rotor according to any one of the aspects (1) to (5).

  According to the aspect of (1), the refrigerant supplied to the shaft is guided in the first flow path and the second flow path as the shaft rotates, and thus flows in the axial direction while flowing in the circumferential direction. . Thereby, the refrigerant guided by the first flow path is supplied to the rotor core. On the other hand, the refrigerant guided by the second flow path is supplied to a portion different from the rotor core. That is, since the refrigerant can be effectively guided to a desired place through the first flow path and the second flow path, the cooling efficiency can be improved.

  According to the aspect (2), the refrigerant is easily stored in the first flow path and the second flow path due to the centrifugal force generated by the rotation of the shaft. Therefore, it becomes easy to effectively supply the refrigerant to a desired place through the first flow path and the second flow path.

  According to the aspect of (3), the refrigerant can be independently circulated in each flow path. Therefore, the refrigerant at a desired flow rate can be easily guided in each flow path, and the degree of freedom in the formation position of each flow path and the supply location of the refrigerant can be improved.

  According to the above aspect (4), since the cross-sectional area of the flow path can be made different between the first flow path and the second flow path, it is easy to supply a desired flow rate of refrigerant to a desired place.

  According to the aspect of (5), by supplying the coolant to the shaft support, cooling of the shaft support and lubricity of the shaft support can be improved.

  According to the above aspect (6), since the rotor of the above aspect is provided, it is possible to provide a rotating electric machine having excellent cooling efficiency.

It is a sectional view showing the schematic structure of the rotary electric machine concerning a 1st embodiment. FIG. 2 is a partial cross-sectional view of the rotating electric machine according to the first embodiment. It is a fragmentary sectional view of the rotary electric machine concerning a 2nd embodiment.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. In addition, about the structure corresponding to each embodiment demonstrated below, the same code | symbol is attached | subjected and description may be abbreviate | omitted.
(1st Embodiment)
FIG. 1 is a cross-sectional view illustrating a schematic configuration of the rotating electric machine 1 according to the first embodiment.
The rotating electric machine 1 shown in FIG. 1 is a traveling motor mounted on a vehicle such as a hybrid vehicle or an electric vehicle. However, the configuration of the present invention is not limited to a traveling motor, but is also applicable to a power generation motor, a motor for other uses, and a rotating electric machine (including a generator) other than a vehicle.

  The rotating electric machine 1 includes a case 2, a stator 3, a rotor 4, and a coolant supply unit 5 (see FIG. 2). In the following description, a direction along an axis C of the shaft 31 described later may be simply referred to as an axial direction, a direction orthogonal to the axis C may be referred to as a radial direction, and a direction around the axis C may be referred to as a circumferential direction.

  The case 2 houses the stator 3 and the rotor 4. The case 2 contains a refrigerant (not shown). The above-mentioned stator 3 is arranged in the case 2 in a state where a part thereof is immersed in the refrigerant. As the refrigerant, ATF (Automatic Transmission Fluid) or the like, which is a hydraulic oil used for lubrication and power transmission of a transmission, is preferably used.

FIG. 2 is a partial cross-sectional view of the rotating electric machine 1.
The stator 3 includes a stator core 11 and a coil 12 mounted on the stator core 11.
Stator core 11 has a cylindrical shape arranged coaxially with axis C. The stator core 11 is fixed to, for example, the inner peripheral surface of the case 2. Stator core 11 is formed by stacking electromagnetic steel sheets in the axial direction. The stator core 11 may be a so-called dust core.

  The coil 12 is mounted on the stator core 11. The coil 12 has a U-phase coil, a V-phase coil, and a W-phase coil arranged with a phase difference of 120 ° from each other in the circumferential direction. The coil 12 has an insertion portion 12a inserted into a slot (not shown) of the stator core 11, and coil end portions 12b and 12c protruding from the stator core 11 in the axial direction. A magnetic field is generated in the stator core 11 when a current flows through the coil 12.

  The rotor 4 is disposed radially inward of the stator 3 with an interval therebetween. The rotor 4 is configured to be rotatable around the axis C. The rotor 4 includes a shaft 31, a rotor core 32, a permanent magnet 33, and end plates (a first end plate 34 and a second end plate 35).

  The shaft 31 is supported by the case 2 so as to be rotatable around the axis C via bearings (a first bearing 41 and a second bearing 42).

  The rotor core 32 is formed in a cylindrical shape arranged coaxially with the axis C. The shaft 31 is press-fitted and fixed inside the rotor core 32. The rotor core 32 may be formed by laminating electromagnetic steel sheets in the axial direction similarly to the stator core 11, or may be a dust core.

  A magnet holding hole 36 that penetrates the rotor core 32 in the axial direction is formed in an outer peripheral portion of the rotor core 32. The plurality of magnet holding holes 36 are formed at intervals in the circumferential direction. A permanent magnet 33 is inserted into each magnet holding hole 36. In addition, a through hole 40 that penetrates the rotor core 32 in the axial direction is formed in an inner peripheral portion of the rotor core 32. A plurality of through holes 40 are formed at intervals in the circumferential direction and the radial direction.

The first end face plate 34 is disposed on the first side in the axial direction with respect to the rotor core 32. The first end face plate 34 covers at least the magnet holding holes 36 in the rotor core 32 from the first side in the axial direction in a state where the first end face plate 34 is press-fitted and fixed to the shaft 31.
The second end face plate 35 is disposed on the second side in the axial direction with respect to the rotor core 32. The second end face plate 35 covers at least the magnet holding holes 36 in the rotor core 32 from the second side in the axial direction in a state where the second end face plate 35 is press-fitted and fixed to the shaft 31. The rotor 4 may have a configuration without the end plates 34 and 35.

<Refrigerant supply section>
The refrigerant supply unit 5 supplies the refrigerant delivered by driving the refrigerant pump to the stator 3, the rotor 4, and the like. The refrigerant pump may be a so-called mechanical pump that is driven in conjunction with the rotation of the shaft 31, or may be a so-called electric pump that is driven independently of the rotation of the shaft 31.

  The coolant supply unit 5 includes a shaft channel 51, a first end plate channel 52, and a second end plate channel 53.

The shaft flow path 51 includes an axial flow path 61, a first discharge port 62, and a second discharge port 63.
The axial channel 61 extends axially at a position that is coaxial with the axis C in the shaft 31. Refrigerant sent from the refrigerant pump flows in the axial center channel 61 along the axial direction.

  The first discharge port 62 is formed in the shaft 31 at a position equivalent to the first end face plate 34 in the axial direction. The first discharge port 62 extends the shaft 31 in the radial direction. A radially inner end of the first discharge port 62 communicates with the axial flow path 61. The radially outer end of the first discharge port 62 opens on the outer peripheral surface of the shaft 31. The refrigerant flowing in the axial flow path 61 flows into the first discharge port 62.

  The second discharge port 63 is formed in the shaft 31 near the second bearing 42 in the axial direction. In the present embodiment, a part of the second discharge port 63 overlaps with the second bearing 42 when viewed from the radial direction. The second discharge port 63 extends the shaft 31 in the radial direction. A radially inner end of the second discharge port 63 communicates with the axial flow path 61. The radially outer end of the second discharge port 63 is open on the outer peripheral surface of the shaft 31. The refrigerant flowing in the axial flow path 61 flows into the second discharge port 63.

  The first end face channel 52 allows the refrigerant flowing from the first discharge port 62 to flow from the inside in the radial direction to the outside by the centrifugal force caused by the rotation of the rotor 4. Specifically, the first end plate channel 52 mainly includes a rotor inlet channel 71 and a stator supply channel 72.

  The rotor inlet channel 71 extends the first end face plate 34 in the radial direction. A radially inner end of the rotor inlet flow passage 71 communicates with the first discharge port 62 described above. That is, the refrigerant flowing through the first discharge port 62 flows into the rotor inlet channel 71. A radially outer end of the rotor inlet channel 71 terminates at an outer peripheral portion of the first end face plate 34.

  The rotor inlet channel 71 is open on a surface of the first end plate 34 facing the rotor core 32. The rotor inlet channel 71 communicates with the above-described through hole 40. The refrigerant flowing in the rotor inlet channel 71 can flow into the through-hole 40 in the process of flowing outward in the radial direction. That is, the through hole 40 also functions as a cooling passage for cooling the rotor core 32.

  The stator supply passage 72 is connected to a downstream end (radially outer end) of the rotor inlet passage 71. The stator supply path 72 passes through the inside of the first end face plate 34 in the axial direction. That is, the above-described rotor inlet channel 71 communicates with the outside of the rotor 4 through the stator supply channel 72.

The second end face channel 53 discharges the refrigerant flowing inside the rotor 4 from the rotor 4 by, for example, centrifugal force caused by the rotation of the rotor 4. The second end face plate channel 53 has a merging channel 81 and a stator supply channel 82.
The joining flow path 81 extends in the second end face plate 35 in the radial direction. The joining flow path 81 is open on the surface of the second end face plate 35 facing the rotor core 32. The joining flow path 81 communicates with the magnet holding hole 36 and the through hole 40 described above.

  The stator supply path 82 communicates with a radially outer end of the joining flow path 81. The stator supply path 82 passes through the second end plate 35 in the axial direction. That is, the above-described merging flow path 81 communicates with the outside of the rotor 4 through the stator supply path 82. Note that the first end plate channel 52 and the second end plate channel 53 may be formed in a plurality in the circumferential direction.

Here, in the present embodiment, two spiral grooves (a first spiral groove (a first flow path) 91 and a second spiral groove (a second flow path)) are formed on the inner peripheral surface of the above-described axial flow path 61. 92) are formed.
The first spiral groove 91 extends in the axial direction while extending in the circumferential direction on the inner peripheral surface of the axial flow channel 61. The upstream end of the first spiral groove 91 is located on the second side in the axial direction with respect to the second bearing 42. On the other hand, the downstream end of the first spiral groove 91 communicates with the above-described first discharge port 62 on the inner peripheral surface of the axial flow path 61. Note that the first spiral groove 91 does not necessarily need to communicate with the first discharge port 62 as long as the configuration guides the refrigerant toward the first discharge port 62.

The pitch P1 (the distance between the centers of adjacent grooves) of the first spiral groove 91 can be changed as appropriate.
In the first helical groove 91 of the present embodiment, the cross-sectional area of the flow path orthogonal to the circumferential direction (the product of the groove width in the axial direction and the depth in the radial direction) is uniformly formed throughout. However, the flow path cross-sectional area of the first spiral groove 91 may be changed in the flow direction.

  The second spiral groove 92 extends in the axial direction while extending in the circumferential direction on the inner peripheral surface of the axial flow path 61. Specifically, the pitch P2 of the second spiral groove 92 is set to be equal to that of the first spiral groove 91. The second spiral groove 92 extends in parallel with the first spiral groove 91 between adjacent grooves of the first spiral groove 91.

  The upstream end of the second spiral groove 92 is located on the second axial side with respect to the second bearing 42. On the other hand, the downstream end of the second spiral groove 92 communicates with the above-described second discharge port 63 on the inner peripheral surface of the axial flow path 61. Note that the second spiral groove 92 does not necessarily need to be in communication with the second discharge port 63 as long as it guides the refrigerant toward the second discharge port 63.

  The second helical groove 92 is formed so that the cross-sectional area of the flow path orthogonal to the circumferential direction (the product of the groove width in the axial direction and the depth in the radial direction) is uniform throughout. However, the flow path cross-sectional area of the second spiral groove 92 may be changed in the flow direction. In the second spiral groove 92 of the present embodiment, at least one of the groove width and the depth is smaller than that of the first spiral groove 91, so that the flow path cross-sectional area is smaller than that of the first spiral groove 91. I have. In addition, the magnitude relation of the flow path cross-sectional area of the first spiral groove 91 and the second spiral groove 92 can be appropriately changed according to the flow rate of the refrigerant to be supplied to the first discharge port 62 and the second discharge port 63.

  The first spiral groove 91 and the second spiral groove 92 are formed in a triangular shape in a longitudinal sectional view along the axial direction. However, the shape of the first spiral groove 91 and the second spiral groove 92 in a longitudinal sectional view may be a rectangular shape, a semicircular shape, or the like. Further, in the present embodiment, a configuration in which the first discharge port 62 communicates with the downstream end of the first spiral groove 91 and the second discharge port 63 communicates with the downstream end of the second spiral groove 92 has been described. It is not limited only to this configuration. That is, a configuration may be employed in which the first spiral groove 91 communicates with the first discharge port 62 halfway, and the second spiral groove 92 communicates with the second discharge port 63 halfway.

[Action]
Next, the operation of the rotating electric machine 1 will be described.
First, the refrigerant flowing through the axial flow path 61 of the shaft flow path 51 mainly travels on the inner peripheral surface of the axial flow path 61 in the axial direction due to the operation of the refrigerant pump and the centrifugal force accompanying the rotation of the rotor 4. It flows from the second side to the first side. At this time, of the refrigerant traveling on the inner peripheral surface of the axial flow path 61, the refrigerant accommodated in the first helical groove 91 is guided along the first helical groove 91 in the circumferential direction while being guided in the axial direction. It is led to one side. On the other hand, of the refrigerant traveling on the inner peripheral surface of the axial flow path 61, the refrigerant accommodated in the second spiral groove 92 is guided along the second spiral groove 92 in the circumferential direction while the first refrigerant in the axial direction. Guided to the side.

  The refrigerant guided to the first spiral groove 91 flows into the first discharge port 62. The refrigerant that has flowed into the first discharge port 62 flows radially outward through the first discharge port 62, and then flows into the rotor inlet channel 71 of the first end plate channel 52. In the first end plate channel 52, the refrigerant flows from the radially inner side to the outer side due to the centrifugal force caused by the rotation of the rotor 4.

  Some of the refrigerant flowing into the rotor inlet passage 71 flows into the stator supply passage 72 in the process of flowing radially outward in the rotor inlet passage 71. The refrigerant flowing into the stator supply path 72 is discharged to the outside of the rotor 4 through the stator supply path 72. The refrigerant discharged from the stator supply path 72 scatters radially outward due to centrifugal force and is supplied to the coil end portion 12b located on the first side in the axial direction with respect to the stator core 11. Thereby, the coil end part 12b is cooled.

  On the other hand, a part of the refrigerant flowing into the rotor inlet passage 71 flows into the through hole 40 in a process of flowing radially outward in the rotor inlet passage 71. The refrigerant that has flowed into the through hole 40 flows in the through hole 40 toward the second side in the axial direction. Thereby, the rotor 4 is cooled. The refrigerant that has passed through the through hole 40 flows into the merging channel 81. The refrigerant that has flowed into the merged flow path 81 flows radially outward in the merged flow path 81, and is then discharged to the outside of the rotor 4 through the stator supply path 82. The refrigerant discharged from the stator supply path 82 is scattered radially outward by centrifugal force and is supplied to the coil end portion 12c located on the second axial side with respect to the stator core 11. Thereby, the coil end part 12c is cooled.

  Further, the refrigerant guided to the second spiral groove 92 flows into the second discharge port 63. The refrigerant flowing into the second discharge port 63 flows to the second discharge port 63 radially outward, and is then supplied to the second bearing 42. Thereby, the second bearing 42 is cooled. Note that the refrigerant supplied to the second bearing 42 may be subsequently supplied to a speed reduction mechanism (not shown) housed in the case 2 or the like.

Thus, in the present embodiment, the first spiral groove 91 and the second spiral groove 92 are formed on the inner peripheral surface of the shaft 31.
According to this configuration, the refrigerant supplied to the shaft 31 is guided in the first spiral groove 91 and the second spiral groove 92 with the rotation of the shaft 31, so that the refrigerant flows in the axial direction while flowing in the circumferential direction. . Thereby, the refrigerant can be supplied to the rotor core 32 through the first spiral groove 91, and the refrigerant can be supplied to the second bearing 42 through the second spiral groove 92. That is, since the refrigerant can be effectively guided to the desired location through the first spiral groove 91 and the second spiral groove 92, the cooling efficiency can be improved. In addition, the lubrication of the second bearing 42 can be improved by supplying the refrigerant to the second bearing 42.

In the present embodiment, the first spiral groove 91 and the second spiral groove 92 are formed on the inner peripheral surface of the shaft 31.
According to this configuration, the refrigerant is easily stored in the first spiral groove 91 and the second spiral groove 92 due to the centrifugal force caused by the rotation of the shaft 31. Therefore, it becomes easy to effectively supply the coolant to a desired location through the first spiral groove 91 and the second spiral groove 92.

In the present embodiment, the configuration is such that the two spiral grooves 91 and 92 extend in parallel.
According to this configuration, the refrigerant can be independently circulated in each of the spiral grooves 91 and 92. Therefore, the refrigerant at a desired flow rate can be easily guided by the spiral grooves 91 and 92, and the degree of freedom in the formation positions of the spiral grooves 91 and 92 and the supply location of the refrigerant can be improved.

In the present embodiment, the first spiral groove 91 and the second spiral groove 92 are configured such that at least one of the groove width and the depth differs.
According to this configuration, the flow path cross-sectional area can be made different between the first spiral groove 91 and the second spiral groove 92, so that it is easy to supply a desired flow rate of refrigerant to a desired place.

  Since the rotating electric machine 1 of the present embodiment includes the rotor 4 described above, the rotating electric machine 1 having excellent cooling efficiency can be provided.

(2nd Embodiment)
FIG. 3 is a partial cross-sectional view of the rotating electric machine 1 according to the second embodiment. This embodiment is different from the above-described first embodiment in that spiral grooves 91 and 92 are formed on the outer peripheral surface of the shaft 31.
In the rotary electric machine 1 shown in FIG. 3, a discharge port 100 is formed in a portion of the shaft 31 located on the second side in the axial direction with respect to the second bearing 42. The discharge port 100 passes through the shaft 31 in the radial direction. On the outer peripheral surface of the shaft 31, a concave portion 101 that is depressed inward in the radial direction is formed. The recess 101 communicates with the discharge port 100 described above.

Each of the spiral grooves 91 and 92 is formed on the outer peripheral surface of the shaft 31. The upstream end of the first spiral groove 91 communicates with the above-described recess 101. The downstream end of the first spiral groove 91 communicates with the above-described rotor inlet channel 71.
On the other hand, the upstream end of the second spiral groove 92 communicates with the above-described recess 101. The downstream end of the second spiral groove 92 overlaps with the second bearing 42 in a longitudinal sectional view.

In the shaft 31 according to the present embodiment, the collar (first) is formed in a region other than the region where the rotor core 32, the end plates 34, 35, and the second bearing 42 are fixed, in the region where the spiral grooves 91, 92 are formed. A collar 110 and a second collar 111) are provided.
The first collar 110 is attached to a portion of the shaft 31 that is located on a second axial side of the second bearing 42. The first collar 110 covers the concave portion 101 and the spiral grooves 91 and 92 from the outside in the radial direction.
The second collar 111 is mounted on a region of the shaft 31 located between the second end face plate 35 and the second bearing 42. The second collar 111 covers the spiral grooves 91 and 92 from the outside in the radial direction.

  In the present embodiment, at least a part of the refrigerant flowing through the axial flow path 61 is supplied into the recess 101 through the discharge port 100. The coolant supplied into the recess 101 is distributed into the spiral grooves 91 and 92.

The refrigerant distributed in the first spiral groove 91 flows toward the first side in the axial direction while being guided in the circumferential direction by centrifugal force caused by the rotation of the shaft 31. The refrigerant flowing in the first spiral groove 91 flows through the end face plates 34 and 35 and the rotor core 32 through the rotor inlet channel 71 as in the first embodiment, and is then discharged to the outside of the rotor 4.
On the other hand, the refrigerant distributed in the second spiral groove 92 flows toward the first side in the axial direction while being guided in the circumferential direction by centrifugal force caused by the rotation of the shaft 31. The refrigerant flowing in the second spiral groove 92 is supplied to the second bearing 42 as in the first embodiment, and then supplied to a speed reduction mechanism or the like.

  Even when the spiral grooves 91 and 92 are formed on the outer peripheral surface of the shaft 31 as in the present embodiment, the same operation and effect as those of the above-described embodiment can be obtained.

(Other modifications)
The preferred embodiments of the present invention have been described above, but the present invention is not limited to these embodiments. Additions, omissions, substitutions, and other modifications of the configuration can be made without departing from the spirit of the present invention. The present invention is not limited by the above description, but is limited only by the appended claims.
For example, in the above-described embodiment, a configuration in which two spiral grooves 91 and 92 are formed has been described. However, the configuration is not limited to this configuration. Three or more spiral grooves may be formed.
In the above-described embodiment, the configuration in which the refrigerant is guided to the rotor core 32 and the second bearing 42 through the spiral grooves 91 and 92 has been described. However, the configuration is not limited to this configuration. For example, when a plurality of rotating electric machines (for example, for traveling and power generation) are mounted in the case 2, the refrigerant may be supplied to the rotor core of each rotating electric machine through the spiral groove. Further, the coolant may be supplied to each of the bearings 41 and 42 through the spiral groove.

In the above-described embodiment, a configuration in which a plurality of spiral grooves extend in parallel has been described, but the present invention is not limited to this configuration. That is, a configuration in which a plurality of spiral grooves extend in series may be used. For example, a configuration may be employed in which the downstream end of the first spiral groove is connected to the upstream end of the second spiral groove.
In the above-described embodiment, the configuration in which the plurality of spiral grooves are formed on only one of the inner peripheral surface and the outer peripheral surface of the shaft 31 has been described. However, the configuration is not limited to this configuration. For example, the first spiral groove may be formed on the inner peripheral surface of the shaft 31 and the second spiral groove may be formed on the outer peripheral surface of the shaft 31.

  In the above-described embodiment, the configuration in which the refrigerant in the axial flow path 61 is supplied to the spiral grooves 91 and 92 has been described. However, the configuration is not limited to this configuration. For example, the coolant may be supplied to the spiral grooves 91 and 92 from the outside of the shaft 31 through a supply port provided in the case 2 or the like.

  In addition, it is possible to appropriately replace the components in the above-described embodiment with well-known components without departing from the spirit of the present invention, and the above-described modifications may be appropriately combined.

DESCRIPTION OF SYMBOLS 1 ... Rotating electric machine 4 ... Rotor 31 ... Shaft 32 ... Rotor core 42 ... 2nd bearing (shaft support part)
62 first discharge port 63 second discharge port 91 first spiral groove (first flow path)
92... Second spiral groove (second flow path)

Claims (6)

A shaft extending along an axis;
A rotor core fixed to the shaft,
On the peripheral surface of the shaft,
A first flow path that extends helically along the axis and guides the refrigerant toward the rotor core;
A second flow path that extends spirally along the axis and guides the refrigerant toward a portion different from the rotor core. The shaft is formed in a cylindrical shape,
The first flow path and the second flow path are formed on an inner peripheral surface of the shaft,
In the shaft,
A first discharge port communicating with the first flow path and opening on an outer peripheral surface of the shaft;
2. The rotor according to claim 1, wherein a second discharge port communicating with the second flow path and opening on an outer peripheral surface of the shaft is formed. 3.   The rotor according to claim 1, wherein the first flow path and the second flow path extend in parallel.   4. The rotor according to claim 1, wherein the first flow path and the second flow path are different in at least one of a width in an axial direction and a depth in a radial direction. 5. A shaft supporting portion that supports the shaft rotatably around an axis,
The rotor according to any one of claims 1 to 4, wherein the second flow path guides a coolant to the shaft support.   A rotary electric machine comprising the rotor according to any one of claims 1 to 5.

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