CN210120441U - Rotor and rotating electrical machine - Google Patents

Abstract

The utility model provides a rotor and rotating electrical machines can supply with the refrigerant to the place that expects effectively. The utility model discloses a rotor (4) include along axle (31) of axis (C) extension and fix rotor core (32) at axle (31). An inner peripheral surface of the shaft (31) is provided with: a first spiral groove (91) that extends spirally along the axis (C) and guides the refrigerant toward the rotor core (32); and a second spiral groove (92) that extends spirally along the axis (C) and guides the refrigerant toward the second bearing (42).

Description

Rotor and rotating electrical machine

Technical Field

The utility model relates to a rotor and rotating electrical machines.

Background

In a rotating electrical machine, a magnetic field is formed in a stator core by supplying a current to a coil, and a magnetic attractive force or repulsive force is generated between a permanent magnet of a rotor and the stator core. Thereby, the rotor rotates relative to the stator.

In the rotating electric machine, the rotor generates heat due to the influence of eddy current or the like generated in the magnet during rotation. When the magnetic force is reduced (so-called thermal demagnetization) due to heat generation of the magnet, the performance of the rotating electric machine may be reduced.

Here, for example, patent document 1 below discloses a structure in which a spiral groove is formed in the 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 portion of the shaft flows into the second side end portion through the spiral groove, and then turns back at the second side end portion to return to the first side end portion. This increases the contact area between the rotor and the refrigerant (spiral groove).

[ Prior art documents ]

[ patent document ]

[ patent document 1] Japanese patent laid-open publication No. 2015-534803

SUMMERY OF THE UTILITY MODEL

[ problem to be solved by the utility model ]

However, in the conventional technology, there is still room for improvement in that the refrigerant is efficiently supplied to a desired place.

An object of the utility model is to provide a can supply rotor and rotating electrical machines of refrigerant to the place that expects effectively.

[ means for solving problems ]

(1) In order to achieve the above object, a rotor (e.g., a rotor 4 in an embodiment) according to an embodiment of the present invention includes a shaft (e.g., a shaft 31 in an embodiment) extending along an axis line and a rotor core (e.g., a rotor core 32 in an embodiment) fixed to the shaft, and the shaft has a circumferential surface on which: a first flow path (for example, a first spiral groove 91 in the embodiment) that extends spirally along the axis and guides a refrigerant toward the rotor core; and a second flow path (for example, a second spiral groove 92 in the embodiment) that extends spirally along the axis and guides the refrigerant to a portion (for example, a second bearing 42 in the embodiment) different from the rotor core.

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

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

(4) In the rotor according to any one of the embodiments (1) to (3), the first flow channel and the second flow channel may be different in at least one of width in the axial direction and depth in the radial direction.

(5) The rotor according to any one of the embodiments (1) to (4) may include a shaft support portion (for example, the second bearing 42 in the embodiment) that supports the shaft rotatably around the axis, and the second flow path may guide the refrigerant to the shaft support portion.

(6) The rotating electrical machine according to an embodiment of the present invention includes the rotor according to any one of the embodiments (1) to (5).

[ effects of the utility model ]

According to the embodiment of (1), the refrigerant supplied to the shaft is guided to the first flow path and the second flow path along with the rotation of the shaft, and 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, the refrigerant can be efficiently guided to a desired place through the first flow path and the second flow path, and thus cooling efficiency can be improved.

According to the embodiment of (2), the refrigerant is easily accommodated in the first flow path and the second flow path by the centrifugal force accompanying the rotation of the shaft. Therefore, the refrigerant can be efficiently supplied to a desired place through the first flow path and the second flow path.

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

According to the embodiment of (4), since the sectional areas of the flow paths can be made different between the first flow path and the second flow path, a desired flow rate of the refrigerant can be easily supplied to a desired place.

According to the embodiment of (5), the lubricating property of the shaft support portion can be improved in addition to the cooling of the shaft support portion by supplying the refrigerant to the shaft support portion.

According to the embodiment (6), since the rotor of the embodiment is included, a rotating electrical machine excellent in cooling efficiency can be provided.

Drawings

Fig. 1 is a sectional view showing a schematic configuration of a rotating electric machine according to a first embodiment.

Fig. 2 is a partial sectional view of the rotating electric machine of the first embodiment.

Fig. 3 is a partial sectional view of a rotating electric machine of a second embodiment.

Description of the symbols

1: rotating electrical machine

4: rotor

31: shaft

32: rotor core

42: second bearing

62: a first discharge port

63: second discharge port

91: first helical groove

92: second helical groove

Detailed Description

Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the embodiments described below, the same reference numerals are given to corresponding components, and the description thereof may be omitted.

(first embodiment)

Fig. 1 is a sectional view showing a schematic configuration of a rotating electric machine 1 according to a first embodiment.

A rotating electric machine 1 shown in fig. 1 is a running motor mounted on a vehicle such as a hybrid vehicle or an electric vehicle. However, the structure of the present invention is not limited to the motor for traveling, and may be applied to a motor for power generation, a motor for other applications, and a rotating electrical machine (including a generator) other than a vehicle.

The rotating electric machine 1 includes: a housing 2, a stator 3, a rotor 4, and a refrigerant supply portion 5 (see fig. 2). In the following description, a direction along the axis C of the shaft 31 described later may be simply referred to as an axial direction, a direction perpendicular to the axis C may be referred to as a radial direction, and a direction about the axis C may be referred to as a circumferential direction.

The housing 2 accommodates the stator 3 and the rotor 4. A refrigerant (not shown) is accommodated in the casing 2. The stator 3 is disposed in the housing 2 in a state in which a part thereof is immersed in the refrigerant. As the refrigerant, an Automatic Transmission Fluid (ATF) or the like, which is a working Fluid used for lubrication of a Transmission, power Transmission, or the like, can be suitably used.

Fig. 2 is a partial 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.

The stator core 11 is cylindrical and disposed coaxially with the axis C. The stator core 11 is fixed to, for example, an inner peripheral surface of the housing 2. Stator core 11 is formed by laminating electromagnetic steel plates in the axial direction. The stator core 11 may be a so-called dust core.

A coil 12 is mounted on the stator core 11. The coil 12 includes a U-phase coil, a V-phase coil, and a W-phase coil arranged with a phase difference of 120 ° therebetween in the circumferential direction. The coil 12 includes an insertion portion 12a inserted into a slit (not shown) of the stator core 11, and a coil end portion 12b and a coil end portion 12c protruding from the stator core 11 in the axial direction. A magnetic field is generated in the stator core 11 by the current flowing in the coil 12.

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

The shaft 31 is rotatably supported around the axis C by the housing 2 via bearings (a first bearing 41 and a second bearing 42).

The rotor core 32 is formed in a cylindrical shape disposed coaxially with the axis C. The fixed shaft 31 is press-fitted into the rotor core 32. The rotor core 32 may be formed by laminating electromagnetic steel plates in the axial direction, as in 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 the outer peripheral portion of the rotor core 32. A plurality of magnet holding holes 36 are formed at intervals in the circumferential direction. Permanent magnets 33 are inserted into the magnet holding holes 36. Further, a through hole 40 that penetrates rotor core 32 in the axial direction is formed in the inner peripheral portion of rotor core 32. A plurality of through holes 40 are formed at intervals in the circumferential direction and the radial direction.

The first end plate 34 is disposed on a first side in the axial direction with respect to the rotor core 32. The first end plate 34 covers at least the magnet holding hole 36 of the rotor core 32 from the first side in the axial direction in a state of being press-fitted and fixed to the shaft 31.

The second end plate 35 is disposed on the second side in the axial direction with respect to the rotor core 32. The second end plate 35 covers at least the magnet holding hole 36 of the rotor core 32 from the second side in the axial direction in a state of being press-fitted and fixed to the shaft 31. The rotor 4 may not have the first end plate 34 and the second end plate 35.

< refrigerant supply part >

The refrigerant supply unit 5 supplies the refrigerant, which is sent out 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 refrigerant supply portion 5 includes: a shaft flow path 51, a first end plate flow path 52, and a second end plate flow path 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 flow path 61 extends in the axial direction in the shaft 31 to be coaxial with the axis C. In the axial flow path 61, the refrigerant pumped from the refrigerant pump flows in the axial direction.

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

The second discharge port 63 is formed in the vicinity of the second bearing 42 in the axial direction in the shaft 31. In the present embodiment, a part of the second discharge port 63 and the second bearing 42 overlap each other when viewed in the radial direction. The second discharge port 63 extends radially in the shaft 31. The radially inner end of the second discharge port 63 communicates with the axial flow path 61. The outer end of the second discharge port 63 in the radial direction opens on the outer peripheral surface of the shaft 31. The refrigerant flowing through the axial flow path 61 flows into the second discharge port 63.

The first end plate flow path 52 causes the refrigerant flowing in from the first discharge port 62 to flow radially inward and outward by centrifugal force caused by rotation of the rotor 4. Specifically, the first end plate passage 52 mainly includes a rotor inlet passage 71 and a stator supply passage 72.

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

The rotor inlet flow path 71 opens on a surface of the first end plate 34 facing the rotor core 32. The rotor inlet flow path 71 communicates with the through-hole 40. The refrigerant flowing through the rotor inlet passage 71 can flow into the through-hole 40 while flowing radially outward. That is, the through-holes 40 also function as cooling passages that cool the rotor core 32.

The stator supply passage 72 is connected to a downstream end (a radially outer end) of the rotor inlet passage 71. The stator feed passage 72 penetrates the first end plate 34 in the axial direction. That is, the rotor inlet channel 71 communicates with the outside of the rotor 4 via the stator supply channel 72.

The second end plate flow passage 53 discharges the refrigerant flowing inside the rotor 4 from the rotor 4 by, for example, a centrifugal force accompanying rotation of the rotor 4. The second end plate flow path 53 has a merged flow path 81 and a stator supply path 82.

The merged channel 81 extends in the radial direction in the second end plate 35. The merged channel 81 is open on the surface of the second end plate 35 facing the rotor core 32. The merged channel 81 is connected to the magnet holding hole 36 or the through hole 40.

The stator supply passage 82 communicates with the outer end of the merged channel 81 in the radial direction. The stator supply channel 82 penetrates the second end plate 35 in the axial direction. That is, the merged channel 81 is communicated to the outside of the rotor 4 via the stator supply channel 82. Further, a plurality of first end plate flow paths 52 or second end plate flow paths 53 may be formed in the circumferential direction.

In the present embodiment, two spiral grooves (a first spiral groove (first flow path) 91 and a second spiral groove (second flow path) 92) are formed on the inner circumferential surface of the axial flow path 61.

The first spiral groove 91 extends in the axial direction while extending in the circumferential direction on the inner peripheral surface of the axial center flow path 61. The upstream end portion of the first spiral groove 91 is located on a second side in the axial direction than the second bearing 42. On the other hand, the downstream end of the first spiral groove 91 is connected to the first discharge port 62 on the inner circumferential surface of the axial flow path 61. The first spiral groove 91 does not necessarily have to be communicated with the first discharge port 62 as long as it is configured to guide the refrigerant toward the first discharge port 62.

The pitch P1 of the first spiral groove 91 (the distance between the centers of adjacent grooves) can be changed as appropriate.

The first spiral groove 91 of the present embodiment is formed so that the cross-sectional area of the flow path (the product of the groove width in the axial direction and the depth in the radial direction) perpendicular to the circumferential direction is uniform over the entire surface. 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 center flow path 61. Specifically, the pitch P2 of the second spiral groove 92 is set equivalent to the first spiral groove 91. The second helical groove 92 extends between adjacent ones of the first helical grooves 91 in parallel with the first helical grooves 91.

The upstream end portion of the second spiral groove 92 is located on a second side in the axial direction than the second bearing 42. On the other hand, the downstream end of the second spiral groove 92 communicates with the second discharge port 63 on the inner circumferential surface of the axial flow path 61. The second spiral groove 92 does not necessarily need to communicate with the second discharge port 63 as long as it is configured to guide the refrigerant to the second discharge port 63.

The second helical groove 92 has a flow path cross-sectional area (the product of the groove width in the axial direction and the depth in the radial direction) perpendicular to the circumferential direction, which is formed uniformly over the entire surface. However, the flow path cross-sectional area of the second helical groove 92 may be changed in the flow direction. In the second helical groove 92 of the present embodiment, at least either the groove width or the depth is smaller than the first helical groove 91, and thus the flow path cross-sectional area is smaller than the first helical groove 91. The magnitude relation of the flow path cross-sectional areas of the first spiral groove 91 and the second spiral groove 92 may 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.

In addition, the first spiral groove 91 and the second spiral groove 92 are formed in a triangular shape in a vertical cross section along the axial direction. However, the first and second spiral grooves 91, 92 may have a rectangular shape, a semicircular shape, or the like in a vertical cross section. In the present embodiment, the description has been given of the structure in which the downstream end portion of the first spiral groove 91 is communicated with the first discharge port 62, and the downstream end portion of the second spiral groove 92 is communicated with the second discharge port 63, but the present invention is not limited to this structure. That is, the first spiral groove 91 may be connected to the first discharge port 62 at a middle portion thereof, and the second spiral groove 92 may be connected to the second discharge port 63 at a middle portion thereof.

[ Effect ]

Next, the operation of the rotating electric machine 1 will be described.

First, the refrigerant flowing through the axial center flow path 61 of the axial flow path 51 is conducted mainly to the inner peripheral surface of the axial center flow path 61 by the action of the refrigerant pump and the centrifugal force accompanying the rotation of the rotor 4, and flows from the second side to the first side in the axial direction. At this time, of the refrigerant conducted on the inner peripheral surface of the axial center flow path 61, the refrigerant accommodated in the first spiral groove 91 is guided to the first side in the axial direction while being guided in the circumferential direction along the first spiral groove 91. On the other hand, among the refrigerants conducted on the inner peripheral surface of the axial center flow path 61, the refrigerant contained in the second spiral groove 92 is guided to the first side in the axial direction while being guided in the circumferential direction along the second spiral groove 92.

The refrigerant guided to the first spiral groove 91 flows into the first discharge port 62. The refrigerant flowing into the first discharge port 62 flows radially outward through the first discharge port 62 and then flows into the rotor inlet flow path 71 of the first end plate flow path 52. In the first end plate flow path 52, the refrigerant flows from the inside to the outside in the radial direction by the centrifugal force accompanying the rotation of the rotor 4.

Of the refrigerant flowing into the rotor inlet passage 71, a part of the refrigerant flows into the stator supply passage 72 while flowing radially outward in the rotor inlet passage 71. The refrigerant flowing into the stator supply passage 72 is discharged to the outside of the rotor 4 through the stator supply passage 72. The refrigerant discharged from the stator supply passage 72 is scattered radially outward by 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 terminal portion 12b is cooled.

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

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 radially outward through the second discharge port 63, and is then supplied to the second bearing 42. Thereby, the second bearing 42 is cooled. The refrigerant supplied to the second bearing 42 may be thereafter supplied to a speed reduction mechanism (not shown) or the like housed in the housing 2.

In this manner, in the present embodiment, the first helical groove 91 and the second helical groove 92 are formed in the inner circumferential surface of the shaft 31.

According to this configuration, the refrigerant supplied to the shaft 31 is guided to the first spiral groove 91 and the second spiral groove 92 with the rotation of the shaft 31, and 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, the refrigerant can be efficiently guided to a desired place through the first and second spiral grooves 91 and 92, and thus the cooling efficiency can be improved. Further, by supplying the refrigerant to the second bearing 42, the lubricity of the second bearing 42 can be improved.

In the present embodiment, the first helical groove 91 and the second helical groove 92 are formed on the inner circumferential surface of the shaft 31.

With this configuration, the refrigerant is easily accommodated in the first spiral groove 91 and the second spiral groove 92 by the centrifugal force accompanying the rotation of the shaft 31. Therefore, the refrigerant can be efficiently supplied to a desired place easily through the first spiral groove 91 and the second spiral groove 92.

In the present embodiment, the first helical groove 91 and the second helical groove 92 extend in parallel.

With this configuration, the refrigerant can independently flow through the first spiral groove 91 and the second spiral groove 92. Therefore, the refrigerant of a desired flow rate is easily guided by the first and second spiral grooves 91 and 92, and the degree of freedom with respect to the positions where the first and second spiral grooves 91 and 92 are formed and the places where the refrigerant is supplied can be improved.

In the present embodiment, at least one of the groove width and the depth is configured to be different in the first spiral groove 91 and the second spiral groove 92.

According to this configuration, since the flow path cross-sectional areas can be made different between the first spiral groove 91 and the second spiral groove 92, the refrigerant can be easily supplied to a desired position at a desired flow rate.

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

(second embodiment)

Fig. 3 is a partial sectional view of the rotating electric machine 1 of the second embodiment. The present embodiment is different from the first embodiment in that the first and second helical grooves 91 and 92 are formed on the outer circumferential surface of the shaft 31.

In the rotating electrical machine 1 shown in fig. 3, a discharge port 100 is formed in a portion of the shaft 31 that is located on a second side in the shaft direction than the second bearing 42. The discharge port 100 radially penetrates the shaft 31. A recess 101 recessed inward in the radial direction is formed in the outer peripheral surface of the shaft 31. The concave portion 101 communicates with the discharge port 100.

First and second spiral grooves 91 and 92 are formed on the outer peripheral surface of the shaft 31. The upstream end of the first spiral groove 91 communicates with the recess 101. The downstream end of the first spiral groove 91 communicates with the rotor inlet passage 71.

On the other hand, an upstream end portion of the second spiral groove 92 communicates with the recess 101. The downstream end portion of the second spiral groove 92 and the second bearing 42 overlap each other as viewed in longitudinal section.

In the shaft 31 of the present embodiment, collars (first collar 110 and second collar 111) are provided in regions other than regions where the rotor core 32, the first end plate 34, the second end plate 35, and the second bearing 42 are fixed, among regions where the first spiral groove 91 and the second spiral groove 92 are formed.

The first collar 110 is mounted on a portion of the shaft 31 located on a second side in the shaft direction than the second bearing 42. The first collar 110 covers the recess 101, the first spiral groove 91, and the second spiral groove 92 from the outside in the radial direction.

A second collar 111 is mounted in the shaft 31 in the region between the second end plate 35 and the second bearing 42. The second collar 111 covers the first and second spiral grooves 91, 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 refrigerant supplied into the recess 101 is distributed into the first and second spiral grooves 91 and 92.

The refrigerant distributed into the first spiral groove 91 flows toward the first side in the axial direction while being guided in the circumferential direction by the centrifugal force accompanying the rotation of the shaft 31. The refrigerant flowing through the first spiral groove 91 flows through the first end plate 34, the second end plate 35, or the rotor core 32 via the rotor inlet passage 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 the centrifugal force accompanying the rotation of the shaft 31. The refrigerant flowing through the second spiral groove 92 is supplied to the second bearing 42 and then supplied to the speed reducing mechanism and the like, as in the first embodiment.

As in the present embodiment, even when the first and second spiral grooves 91 and 92 are formed on the outer peripheral surface of the shaft 31, the same operational advantages as those of the above-described embodiment are obtained.

(other modification example)

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 changes in the structure can be made without departing from the spirit of the invention. The invention is not to be limited by the foregoing description, but is only limited by the scope of the appended claims.

For example, in the above-described embodiment, the configuration in which two spiral grooves (the first spiral groove 91 and the second spiral groove 92) are formed has been described, but the present invention is not limited to this configuration. More than three spiral grooves can be formed.

In the above embodiment, the description has been given of the structure in which the refrigerant is guided to the rotor core 32 and the second bearing 42 via the first and second spiral grooves 91 and 92, but the present invention is not limited to this structure. For example, when a plurality of rotating electric machines (for example, for traveling and power generation) are mounted in the housing 2, the refrigerant may be supplied to the rotor core of each rotating electric machine through the spiral groove. The refrigerant may be supplied to the first bearing 41 and the second bearing 42 through the spiral groove.

In the above embodiment, the configuration in which the plurality of spiral grooves extend in parallel has been described, but the present invention is not limited to this configuration. That is, a plurality of spiral grooves may extend in series. For example, the downstream end of the first spiral groove may be connected to the upstream end of the second spiral groove.

In the above embodiment, the structure in which the plurality of spiral grooves are formed only on either the inner peripheral surface or the outer peripheral surface of the shaft 31 has been described, but the present invention is not limited to this structure. For example, a first spiral groove may be formed on the inner circumferential surface of the shaft 31, and a second spiral groove may be formed on the outer circumferential surface of the shaft 31.

In the above embodiment, the description has been given of the structure in which the refrigerant in the axial flow path 61 is supplied to the first spiral groove 91 and the second spiral groove 92, but the present invention is not limited to this structure. For example, the refrigerant may be supplied from the outside of the shaft 31 to the first and second spiral grooves 91 and 92 through a supply port provided in the housing 2 or the like.

Further, the components in the above embodiments may be replaced with well-known components as appropriate without departing from the scope of the present invention, and the above modifications may be combined as appropriate.

Claims (10)

1. A rotor, comprising:

a shaft elongated along an axis; and

a rotor core fixed to the shaft; and is

The shaft has formed on a circumferential surface thereof:

a first flow path that extends spirally along the axis and guides a refrigerant toward the rotor core; and

and a second flow path that extends spirally along the axis and guides the refrigerant to a portion different from the rotor core.

2. The rotor of claim 1,

the shaft is formed in a cylindrical shape,

the first and second flow passages are formed on an inner peripheral surface of the shaft

The shaft is provided with:

a first discharge port that communicates with the first flow path and opens on an outer peripheral surface of the shaft; and

and a second discharge port that communicates with the second flow path and opens on the outer peripheral surface of the shaft.

3. The rotor of claim 1 or 2,

the first flow path and the second flow path extend in parallel.

4. The rotor of claim 1 or 2,

the first and second flow paths have different widths in the axial direction and different depths in the radial direction.

5. The rotor of claim 3,

the first and second flow paths have different widths in the axial direction and different depths in the radial direction.

6. The rotor of claim 1 or 2, comprising,

a shaft supporting part which supports the shaft rotatably around the axis line and

the second flow path guides the refrigerant to the shaft support portion.

7. The rotor of claim 3, comprising,

a shaft supporting part which supports the shaft rotatably around the axis line and

the second flow path guides the refrigerant to the shaft support portion.

8. The rotor as set forth in claim 4, comprising,

a shaft supporting part which supports the shaft rotatably around the axis line and

the second flow path guides the refrigerant to the shaft support portion.

9. The rotor as set forth in claim 5, comprising,

a shaft supporting part which supports the shaft rotatably around the axis line and

the second flow path guides the refrigerant to the shaft support portion.

10. A rotating electrical machine, characterized by comprising:

a rotor according to any one of claims 1 to 9.

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