JP2008219960A - Rotating electric machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rotary electric machine efficiently removing heat of a conductor or a magnetic pole disposed in an outer circumferential portion of a stator while suppressing deterioration in efficiency of the rotary electric machine. <P>SOLUTION: A coolant feeding port 32 for feeding a liquid coolant to the inside of a rotor 14 is formed on one end of an axial core 22. A heat removing flow passage 36 leading to the coolant feeding port 32 and removing heat of a conductor 18 by a liquid coolant supplied from the coolant feeding port 32 is provided near the conductor 18 in the outer circumferential portion of an iron core 16. A coolant discharge port 40 leading to the heat removing flow passage 36 and discharging the liquid coolant supplied to the heat removing flow passage 36 from the inside of the rotor 14 is formed on the other end of the axial core 22. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a rotating electrical machine, and more particularly to a rotor cooling structure.

  Various structures have been proposed as cooling structures for rotating electrical machines. For example, in Patent Document 1 below, refrigerant is supplied from the shaft center into the rotor, and the refrigerant supplied into the rotor is passed between the rotor and the stator through a refrigerant flow path extending along the radial direction of the rotor. Is supplied to the gap.

  Moreover, in the following Patent Document 2, the rotor core is covered with a case with a predetermined gap, a refrigerant flow path is provided inside the shaft, and an opening of the refrigerant flow path is provided at a position corresponding to the gap. The coolant is supplied from one end of the shaft to the gap between the rotor core and the case via the coolant flow path to cool the rotor core.

  In addition, the cooling structure of the rotary electric machine by the following patent documents 3-7 is disclosed.

JP-A-6-159825 JP-A-9-163682 JP-A-5-49236 JP-A-5-236704 JP-A-9-46973 JP-A-9-9561 JP-A-7-115742

  In Patent Document 1, since the refrigerant is supplied to the gap between the rotor and the stator, when the rotor rotates with respect to the stator, a shearing force acts on the refrigerant to cause drag loss. . As a result, the efficiency of the rotating electrical machine is reduced.

  In Patent Document 2, although drag loss does not occur, it is necessary to use a nonmetallic material for the case in order to suppress the influence of the case covering the rotor core on the magnetic characteristics of the rotor. As a result, the amount of magnetic gap between the rotor and the stator increases, leading to a reduction in efficiency of the rotating electrical machine.

  An object of the present invention is to provide a rotating electrical machine that can efficiently remove heat from a conductor or magnetic pole disposed on an outer peripheral portion of a rotor while suppressing a decrease in efficiency of the rotating electrical machine.

  The rotating electrical machine according to the present invention employs the following means in order to achieve the above-described object.

  A rotating electrical machine according to the present invention is a rotor in which a conductor or a magnetic pole is disposed on an outer periphery of an iron core, the rotor having an axis disposed along the rotation center axis thereof, an outer periphery of the iron core, A refrigerant supply port for supplying a liquid refrigerant to the inside of the rotor, formed at one end of the shaft, and communicated with the refrigerant supply port. A heat removal channel for removing heat from a conductor or magnetic pole disposed on the outer periphery of the iron core by the liquid refrigerant supplied from the iron core is formed in the iron core, communicated with the heat removal channel, and supplied to the heat removal channel The gist is that a refrigerant discharge port for discharging the refrigerant from the inside of the rotor is formed at one end or the other end of the shaft.

  According to the present invention, while suppressing the reduction in efficiency of the rotating electrical machine, the centrifugal force due to the rotation of the rotor and the liquid buoyancy due to the heat received from the rotor are used, so that the conductors or magnetic poles disposed on the outer periphery of the rotor Heat removal can be performed efficiently.

  In one aspect of the present invention, it is preferable that the heat removal flow path includes a pipe-shaped flow path extending from one end side to the other end side of the iron core in a direction parallel to the axis. According to this aspect, since the frictional force acting on the liquid refrigerant flowing through the heat removal flow path can be limited as much as possible in the main flow direction, the transport power of the liquid refrigerant to the rotor can be reduced.

  In one aspect of the present invention, the flow path extends from the shaft center toward the outer peripheral portion of the rotor, the end portion on the shaft center side communicates with the refrigerant supply port, and the end portion on the outer peripheral portion side of the rotor is excluded. A supply-side flow path that communicates with one end of the heat flow path is formed inside the rotor and extends from the shaft center toward the outer periphery of the rotor, and the end on the shaft center side communicates with the refrigerant discharge port. In addition, it is preferable that a discharge-side flow path in which an outer end portion side of the rotor communicates with the other end of the heat removal flow path is formed inside the rotor.

  In one embodiment of the present invention, the contact area between the liquid refrigerant flowing through the heat removal flow path and the rotor is the contact area between the liquid refrigerant flowing through the supply side flow path and the rotor, and the liquid refrigerant flowing through the discharge side flow path and the rotor. It is preferable that it is larger than at least one of the contact areas with the child. According to this aspect, the pressure difference between the refrigerant discharge port and the refrigerant supply port can be increased, and the transport power of the liquid refrigerant to the rotor can be reduced.

  In one aspect of the present invention, at least one of the contact area between the liquid refrigerant flowing through the supply-side flow path and the rotor and the contact area between the liquid refrigerant flowing through the discharge-side flow path and the rotor rotates more than the axial center side. It is preferable that the outer peripheral portion side of the child is larger. Also according to this aspect, the pressure difference between the refrigerant discharge port and the refrigerant supply port can be increased, and the transport power of the liquid refrigerant to the rotor can be reduced.

  In one embodiment of the present invention, it is preferable that a heat insulating member is disposed around at least one of the supply side flow path and the discharge side flow path. Also according to this aspect, the pressure difference between the refrigerant discharge port and the refrigerant supply port can be increased, and the transport power of the liquid refrigerant to the rotor can be reduced. In this aspect, the thickness of the heat insulating member is thicker on the axial center side than on the outer peripheral side of the rotor, so that the pressure difference between the refrigerant discharge port and the refrigerant supply port can be further increased. The power for transporting the liquid refrigerant to the child can be further reduced.

  In one aspect of the present invention, the supply-side flow path is formed at one end of the rotor in a direction parallel to the axis, and the discharge-side flow path is formed at the other end of the rotor in a direction parallel to the axis. It is preferable that In one embodiment of the present invention, the plurality of supply-side flow paths are formed radially and the plurality of discharge-side flow paths are formed radially, and the plurality of heat removal flow paths are arranged in the circumferential direction of the rotor. It is preferred that

  The rotating electrical machine according to the present invention is a rotor having a conductor disposed on the outer peripheral portion thereof, and the rotor having an axis disposed along the rotation center axis thereof, and facing the outer peripheral portion of the rotor. A refrigerant supply port for supplying liquid refrigerant into the rotor is formed at one end of the shaft, communicated with the refrigerant supply port, and from the refrigerant supply port The liquid refrigerant supplied to the heat removal flow path is formed inside the conductor to remove heat from the conductor disposed on the outer peripheral portion of the rotor by the supplied liquid refrigerant and communicates with the heat removal flow path. The gist of the invention is that a refrigerant outlet for discharging the gas from the rotor is formed at one end or the other end of the shaft.

  According to the present invention, the heat removal of the conductor disposed on the outer peripheral portion of the rotor is performed using the centrifugal force due to the rotation of the rotor and the liquid buoyancy due to the heat received from the rotor while suppressing the efficiency reduction of the rotating electrical machine. Can be performed efficiently.

  In one aspect of the present invention, the conductor disposed on the outer peripheral portion of the rotor is a tubular conductor extending from one end side to the other end side of the rotor with respect to the direction parallel to the axis, It is preferable to include a flow path extending along the longitudinal direction of the tubular conductor. According to this aspect, since the frictional force acting on the liquid refrigerant flowing through the heat removal flow path can be limited as much as possible in the main flow direction, the transport power of the liquid refrigerant to the rotor can be reduced.

  The rotating electrical machine according to the present invention is a rotor having a conductor or a magnetic pole disposed on the outer periphery thereof, the rotor having an axis disposed along the rotation center axis thereof, and the outer periphery of the rotor. And a stator disposed oppositely, wherein a refrigerant supply port for supplying liquid refrigerant into the rotor is formed at one end of the shaft, and the liquid refrigerant is discharged from the rotor. A refrigerant discharge port is formed in one end portion or the other end portion of the shaft center, and is a pipe-like flow path extending from the shaft center toward the outer peripheral portion of the rotor, and the end portion on the shaft center side supplies the refrigerant. A heat removal flow path communicating with the opening and the refrigerant discharge port and closed at the outer peripheral portion side of the rotor is formed inside the rotor, and the heat removal flow path is a conductor disposed on the outer peripheral portion of the rotor or As the magnetic pole generates heat, the liquid refrigerant moves the heat from the outer peripheral end of the rotor to the end of the axial center. And summarized in that a flow path for performing conductors or pole heat removal disposed on the outer periphery of the child.

  According to the present invention, by making the heat removal flow path function as a thermosiphon, the rotor is utilized by utilizing the centrifugal force due to the rotation of the rotor and the liquid buoyancy due to the heat received from the rotor while suppressing the efficiency reduction of the rotating electrical machine. It is possible to efficiently remove heat from the conductors or magnetic poles disposed on the outer peripheral portion of the metal.

  In one aspect of the present invention, it is preferable that the heat removal channel is formed at the end of the rotor in a direction parallel to the axis. According to this aspect, the influence of the heat removal channel on the magnetic characteristics of the rotor can be suppressed.

  In one embodiment of the present invention, it is preferable that a plurality of heat removal channels be formed radially.

  DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments for carrying out the present invention (hereinafter referred to as embodiments) will be described with reference to the drawings.

“Embodiment 1”
1-5 is a figure which shows schematic structure of the rotary electric machine which concerns on Embodiment 1 of this invention, and shows the case where this invention is applied to an induction machine. 1 shows an overall schematic configuration as viewed from a direction orthogonal to the axis 22, FIG. 2 shows an external view of the rotor 14, FIG. 3 shows a cross-sectional view taken along the line AA in FIG. 2 shows a cross-sectional view taken along the line BB of FIG. 2, and FIG. 5 shows a cross-sectional view taken along the line CC of FIG. The rotating electrical machine according to this embodiment includes a stator (stator) 12 fixed to a casing 24 and provided with a winding (primary conductor) 26, and is disposed inside the stator 12 and is rotatable with respect to the stator 12. A rotor (rotor) 14.

  Rotor 14 includes an iron core (core) 16, a plurality of conductors (secondary conductors) 18 disposed on the outer periphery of iron core 16, and short-circuit rings 20-1 and 20-2. A shaft center 22 is disposed on the rotor 14 along its rotation center axis, and the shaft center 22 is rotatably supported by a casing 24. One end and the other end of the shaft 22 protrude outside the casing 24. The plurality of conductors 18 are rod-shaped conductors that extend from one end side to the other end side of the iron core 16 in the direction parallel to the axis 22, and are arranged at intervals along the circumferential direction of the rotor 14. Yes. The short-circuit ring 20-1 is disposed at one end of the rotor 14 in the direction parallel to the axis 22, and the short-circuit ring 20-2 is disposed at the other end of the rotor 14 in the direction parallel to the axis 22. It is installed. One end of each conductor 18 is connected to the short-circuit ring 20-1, and the other end of each conductor 18 is connected to the short-circuit ring 20-2. A squirrel-cage conductor is formed by the conductor 18 and the short-circuit rings 20-1 and 20-2. Each conductor 18 may be embedded in the rotor 14 (iron core 16), or may be exposed on the surface (outer peripheral surface) of the rotor 14. Also, the number of conductors 18 disposed on the outer peripheral portion of the iron core 16 can be arbitrarily set.

  The inner peripheral portion of the stator 12 is disposed opposite to the outer peripheral portion (conductor 18) of the iron core 16, and a plurality of windings 26 are disposed along the circumferential direction of the stator 12. When an alternating current flows through the winding 26 of the stator 12, the winding 26 generates a rotating magnetic field that rotates in the circumferential direction of the stator 12, and is induced in the conductor 18 of the rotor 14 as the rotating magnetic field is generated. A current is generated. Due to this rotating magnetic field and induced current, a rotational force acts on the rotor 14 and the rotor 14 rotates. At that time, the rotor 14 generates heat, and in particular, the amount of heat generated at the outer peripheral portion where the conductor 18 is disposed increases.

  In the present embodiment, in order to cool the rotor 14 (particularly the conductor 18 and its surroundings), a liquid refrigerant such as oil is supplied into the rotor 14. Hereinafter, a configuration for cooling the rotor 14 will be described.

  As shown in FIG. 1, a refrigerant supply port 32 for supplying liquid refrigerant into the rotor 14 is formed at one end of the shaft 22. A supply-side flow path 34 that communicates with the refrigerant supply port 32 is formed inside the rotor 14. The supply-side flow path 34 here is a pipe-shaped flow path extending from the shaft center 22 toward the outer peripheral portion of the rotor 14, and is formed at one end of the iron core 16 in a direction parallel to the shaft center 22. . And as shown in FIG. 3, the several supply side flow path 34 extended along the radial direction of the rotor 14 is arrange | positioned radially along the circumferential direction of the rotor 14, Each supply side flow path 34 is as follows. The end of the shaft 22 is in communication with the refrigerant supply port 32.

  Further, as shown in FIG. 1, a heat removal flow path 36 communicating with the refrigerant supply port 32 through the supply side flow path 34 is formed inside the rotor 14 (iron core 16). The heat removal flow path 36 here is a pipe-shaped flow path extending in parallel (or substantially parallel) to the conductor 18 from one end side to the other end side of the iron core 16 in the direction parallel to the axis 22. It is formed in the vicinity. As shown in FIGS. 3 and 5, a plurality of heat removal channels 36 are arranged at intervals along the circumferential direction of the rotor 14, and each heat removal channel 36 is supplied at one end thereof. The side channel 34 communicates with the end of the rotor outer peripheral side. Each heat removal channel 36 can be formed without being brought into contact with (close to) the conductor 18 as shown in FIG. 5, for example, or can be formed with being brought into contact with the conductor 18 as shown in FIG. You can also In addition, each conductor 18 and each heat removal flow path 36 may be parallel to the axis 22 (rotation center axis of the rotor 14), or may be slightly inclined with respect to the direction parallel to the axis 22. Further, the heat removal flow path 36 may not necessarily be provided for each conductor 18, and a plurality of heat removal flow paths 36 may be provided for each conductor 18.

  Further, as shown in FIG. 1, a discharge side flow path 38 communicating with the other end of the heat removal flow path 36 is formed inside the rotor 14. Here, the discharge-side flow path 38 is a pipe-shaped flow path extending from the shaft center 22 toward the outer peripheral portion of the rotor 14, and is formed at the other end of the iron core 16 in a direction parallel to the shaft center 22. Yes. And as shown in FIG. 4, the some discharge side flow path 38 extended along the radial direction of the rotor 14 is arrange | positioned radially along the circumferential direction of the rotor 14, Each discharge side flow path 38 is The other end of each heat removal channel 36 communicates with the end on the rotor outer peripheral side. Further, as shown in FIGS. 1 and 4, the other end portion of the shaft center 22 communicates with the end portion on the shaft center 22 side of each discharge side flow path 38, thereby passing through each discharge side flow path 38. A refrigerant discharge port 40 communicating with each heat removal flow path 36 is formed. The supply-side flow path 34, the heat removal flow path 36, and the discharge-side flow path 38 can be formed by making holes in the iron core 16, or a metal tube whose surface is coated with an insulating film is formed inside the iron core 16. It can also be formed by embedding. Further, the number of supply side flow paths 34, heat removal flow paths 36, and discharge side flow paths 38 formed inside the rotor 14 is arbitrarily set according to the number of conductors 18 and the thermal load of the conductors 18. Can do.

  The liquid refrigerant that has flowed into the rotor 14 from the refrigerant supply port 32 (one end portion of the shaft center 22) by a pump (not shown) is subjected to centrifugal force due to the rotation of the rotor 14, thereby causing each supply-side flow path 34 to flow. And supplied to each heat removal passage 36. The liquid refrigerant supplied to each heat removal flow path 36 removes heat from each conductor 18 (and the surrounding iron core 16) located in the vicinity thereof, and thereby is carried away, whereby each conductor 18 (and further the surrounding iron core). The heat removal of 16) is performed. Along with this heat removal, the liquid refrigerant rises in temperature by receiving heat supply. The liquid refrigerant after being used for heat removal is discharged from the refrigerant discharge port 40 (the other end of the shaft 22) through each supply-side flow path 34. In this way, heat can be removed from the outer peripheral portion of the rotor 14 (conductor 18 and its surroundings) by the liquid refrigerant flowing through each heat removal flow path 36. In that case, since the components in the casing 24 such as the stator 12 are not exposed to the liquid refrigerant, the durability of the rotating electrical machine can be improved. Further, since the liquid refrigerant does not enter the gap between the rotor 14 and the stator 12, drag loss when the rotor 14 rotates with respect to the stator 12 can be reduced. And the heat removal of the outer peripheral part of the rotor 14 can be performed, without increasing the amount of magnetic gaps between the rotor 14 and the stator 12. Furthermore, since the heat removal flow path 36 can be formed by drilling a hole in the iron core 16 (metal), the rotor 14 can be heated in a state of low thermal resistance without incurring the complexity of the structure of the rotor 14. It is possible to efficiently remove heat from the conductor 18 disposed on the outer peripheral portion. Therefore, according to the present embodiment, it is possible to efficiently remove heat from the conductor 18 disposed on the outer peripheral portion of the rotor 14 while suppressing a decrease in efficiency of the rotating electrical machine.

  Further, centrifugal force acts on the liquid refrigerant supplied into the rotor 14 as the rotor 14 rotates. The liquid refrigerant flowing inside the rotor 14 undergoes a change in density due to a change in temperature caused by heat received from the rotor 14. Due to this density change, buoyancy (liquid buoyancy) is generated in the liquid refrigerant. In the present embodiment, the heat of the conductor 18 can be efficiently removed by utilizing the centrifugal force due to the rotation of the rotor 14 and the liquid buoyancy due to the heat received from the rotor 14.

  Note that when the density change occurs in the liquid refrigerant as heat is received from the rotor 14, a pressure difference of the liquid refrigerant occurs between the refrigerant discharge port 40 and the refrigerant supply port 32. If the rotor 14 is in an isothermal field, there is almost no pressure difference between the refrigerant discharge port 40 and the refrigerant supply port 32, and the transport power of the liquid refrigerant to the rotor 14 is almost frictional in the flow path. This is equivalent to the loss. However, in reality, the liquid refrigerant is supplied with heat inside the rotor 14 and rises in temperature, so that the pressure of the liquid refrigerant at the refrigerant discharge port 40 is higher than the pressure of the liquid refrigerant at the refrigerant supply port 32. And the transport power of a liquid refrigerant can be reduced, so that the pressure difference of the refrigerant | coolant discharge | emission port 40 and the refrigerant | coolant supply port 32 is large. Therefore, the inventor of the present application has a heat generation amount distribution (a heat receiving amount distribution) in the supply side flow path 34, the heat removal flow path 36, and the discharge side flow path 38 for increasing the pressure difference between the refrigerant discharge port 40 and the refrigerant supply port 32. ) Was examined by numerical calculation (analysis). Hereinafter, the analysis result will be described.

As shown in FIG. 7, a flow path including a refrigerant supply port 32, a supply side flow path 34, a heat removal flow path 36, a discharge side flow path 38, and a refrigerant discharge port 40 is formed inside the rotating body, and lubricating oil is supplied to the refrigerant. Consider the case of supplying from the port 32 and discharging from the refrigerant discharge port 40. In this case, how the pressure difference between the refrigerant discharge port 40 and the refrigerant supply port 32 changes when the heat generation amount distribution in the supply side flow path 34, the heat removal flow path 36, and the discharge side flow path 38 is changed. It was investigated by numerical calculation. The calculation result is shown in FIG. In Figure 7, 8, Q _A is the fraction of the amount of heat generated at a rate of heating value, the Q _C discharge side flow passage 38 in the ratio of the calorific value, Q _B is Jonetsuryuro 36 in the supply side flow passage 34, Q _{Satisfies A} + Q _B + Q _C = 100%. P1 is the pressure of the refrigerant supply port 32, and P4 is the pressure of the refrigerant discharge port 40. However, in FIG. 8, the pressure P4 of the refrigerant discharge port 40 is atmospheric pressure, and the relationship between the rotational speed of the rotating body and the pressure (inlet pressure) P1 of the refrigerant supply port 32 is shown.

As shown in FIG. 8, the ratio of the calorific value Q _B is increased in Jonetsuryuro 36, feed-side passage 34, the ratio Q _A heating value at the discharge side flow passage 38, as Q _C is decreased, refrigerant supply It can be seen that the pressure P1 at the port 32 decreases and the pressure difference between the refrigerant discharge port 40 and the refrigerant supply port 32 increases. Therefore, by increasing the amount of heat removed by the liquid refrigerant in the heat removal flow path 36 and decreasing the amount of heat removal by the liquid refrigerant in the supply side flow path 34 and the discharge side flow path 38, the refrigerant discharge port 40 and the refrigerant supply port Thus, the pressure difference from the second refrigerant can be increased, and the transport power of the liquid refrigerant can be reduced. In the present embodiment, the amount of heat generated at the outer peripheral portion (conductor 18) of the rotor 14 is larger than the amount of heat generated at both ends (short-circuit rings 20-1 and 20-2) of the rotor 14 in the direction parallel to the axis 22. large. For this reason, the amount of heat removed by the liquid refrigerant in the heat removal flow path 36 is increased compared to the amount of heat removed by the liquid refrigerant in the supply side flow path 34 and the discharge side flow path 38, and the refrigerant discharge port 40 and the refrigerant supply port 32 The pressure difference also increases. As a result, the transport power of the liquid refrigerant to the rotor 14 can be reduced.

  In Patent Document 2, the rotor iron core is provided with a predetermined gap and covered with a case, and the gap between the rotor iron core and the case is a refrigerant flow path through which liquid refrigerant flows. However, since wall friction acts on the liquid refrigerant flowing in the refrigerant flow path (void), secondary flow such as swirl flow and vortex flow along the circumferential direction of the rotor is available in addition to the main flow along the axial direction. A flow occurs. As a result, the transportation power of the liquid refrigerant to the rotor is increased. On the other hand, in the present embodiment, the supply side flow path 34, the heat removal flow path 36, and the discharge side flow path 38 are formed as pipe-shaped flow paths, so that the supply side flow path 34, the heat removal flow path 36, and The wall frictional force acting on the liquid refrigerant flowing through the discharge side flow path 38 can be reduced as much as possible only in the main flow direction (longitudinal direction of the supply side flow path 34, the heat removal flow path 36, and the discharge side flow path 38). . As a result, it is possible to suppress the pressure difference between the refrigerant discharge port 40 and the refrigerant supply port 32 from being reduced by the wall frictional force, and to further reduce the transport power of the liquid refrigerant to the rotor 14.

  Furthermore, in this embodiment, in order to further reduce the amount of heat removed by the liquid refrigerant in the supply side flow path 34, for example, as shown in FIG. 9, a heat insulating member 44 can be provided around the supply side flow path 34. . The heat insulating member 44 can further reduce the amount of heat received by the liquid refrigerant flowing in the supply-side flow path 34, thereby further increasing the pressure difference between the refrigerant discharge port 40 and the refrigerant supply port 32. The transport power of the refrigerant can be further reduced. Similarly, in order to further reduce the amount of heat removed by the liquid refrigerant in the discharge-side flow path 38, a heat insulating member 48 can be provided around the discharge-side flow path 38, for example, as shown in FIG. The heat insulating member 48 can further reduce the amount of heat received by the liquid refrigerant flowing in the discharge side flow path 38, so that the pressure difference between the refrigerant discharge port 40 and the refrigerant supply port 32 can be further increased.

  In the present embodiment, for example, as shown in FIG. 10, the diameter of the heat removal channel 36 is set larger than the diameter of the supply side channel 34 to supply the cross-sectional area (channel area) of the heat removal channel 36. It can also be set larger than the cross-sectional area (channel area) of the side channel 34. As a result, the contact area between the liquid refrigerant flowing in the heat removal flow path 36 and the rotor 14 can be made larger than the contact area between the liquid refrigerant flowing in the supply-side flow path 34 and the rotor 14. The amount of heat removed by the liquid refrigerant in the heat flow path 36 can be further increased. Similarly, for example, as shown in FIG. 10, the diameter of the heat removal flow path 36 is set larger than the diameter of the discharge side flow path 38, and the sectional area (flow path area) of the heat removal flow path 36 is set to the discharge side flow path 38. Can be set larger than the cross-sectional area (channel area). As a result, the contact area between the liquid refrigerant flowing through the heat removal flow path 36 and the rotor 14 can be made larger than the contact area between the liquid refrigerant flowing through the discharge side flow path 38 and the rotor 14. The amount of heat removed by the liquid refrigerant in the heat flow path 36 can be further increased.

Further, as shown in FIGS. 11A to 11D, the inventor of the present application changes the refrigerant discharge port 40 and the refrigerant when the heat generation amount distribution in the supply side flow path 34 and the heat generation amount distribution in the discharge side flow path 38 are changed. It was examined by numerical calculation how the pressure difference with the supply port 32 changes. The calculation result is shown in FIG. The calorific value distribution (distribution 1) shown in FIG. 11A gradually increases as the ratio Q _A of the calorific value in the supply-side flow path 34 moves from the axial center 22 side toward the outer peripheral side, and the calorific value distribution in the discharge-side flow path 38. The distribution is such that the ratio Q _C gradually increases from the axial center 22 side toward the outer peripheral side. The calorific value distribution (distribution 2) shown in FIG. 11B gradually increases as the ratio Q _A of the calorific value in the supply-side flow path 34 moves from the axial center 22 side to the outer peripheral side, and the calorific value distribution in the discharge-side flow path 38. The distribution is such that the ratio Q _C gradually decreases from the axial center 22 side toward the outer peripheral side. The calorific value distribution (distribution 3) shown in FIG. 11C gradually decreases as the ratio Q _A of the calorific value in the supply-side flow path 34 moves from the axial center 22 side toward the outer peripheral side, and the calorific value distribution in the discharge-side flow path 38. The distribution is such that the ratio Q _C gradually increases from the axial center 22 side toward the outer peripheral side. The calorific value distribution (distribution 4) shown in FIG. 11D gradually decreases as the ratio Q _A of the calorific value in the supply-side flow path 34 moves from the axial center 22 side toward the outer peripheral side, and the calorific value distribution in the discharge-side flow path 38. The distribution is such that the ratio Q _C gradually decreases from the axial center 22 side toward the outer peripheral side. 11A to 11D (distributions 1 to 4), the ratio Q _B of the heat generation amount in the heat removal channel 36 is uniform. Also in FIG. 12, the pressure P4 of the refrigerant discharge port 40 is the atmospheric pressure, and the relationship between the rotational speed of the rotating body and the pressure (inlet pressure) P1 of the refrigerant supply port 32 is shown.

  As shown in FIG. 12, the heat generation amount distribution (distribution 2, 3) shown in FIGS. 11B and 11C has a lower pressure P1 at the refrigerant supply port 32 than the heat generation amount distribution (distribution 4) shown in FIG. 11D. It can be seen that the heat generation amount distribution (distribution 1) shown in FIG. 11A has a lower pressure P1 at the refrigerant supply port 32 than the heat generation amount distributions (distribution 2 and 3) shown in FIGS. 11B and 11C. Therefore, the amount of heat removed by the liquid refrigerant in the supply-side flow path 34 is increased on the outer peripheral portion side of the rotor 14 than on the shaft center 22 side, so that the pressure difference between the refrigerant discharge port 40 and the refrigerant supply port 32 is increased. Can be increased, and the transport power of the liquid refrigerant can be reduced. Similarly, the amount of heat removed by the liquid refrigerant in the discharge-side flow path 38 is increased on the outer peripheral portion side of the rotor 14 than on the shaft center 22 side, whereby the pressure between the refrigerant discharge port 40 and the refrigerant supply port 32 is increased. The difference can be increased.

  Therefore, in the present embodiment, for example, as shown in FIG. 13, the thickness of the heat insulating member 44 disposed around the supply-side flow path 34 is set closer to the axis 22 side than the outer peripheral side of the rotor 14. Can also be made thicker. As a result, the amount of heat removed by the liquid refrigerant in the supply-side flow path 34 is larger on the outer peripheral portion side of the rotor 14 than on the shaft center 22 side. Similarly, for example, as shown in FIG. 13, the thickness of the heat insulating member 48 disposed around the discharge side flow path 38 is made thicker on the shaft center 22 side than on the outer peripheral side of the rotor 14. You can also. As a result, the amount of heat removed by the liquid refrigerant in the discharge-side flow path 38 is larger on the outer peripheral portion side of the rotor 14 than on the shaft center 22 side. FIG. 13 shows an example in which the thickness of the heat insulating members 44 and 48 gradually increases from the outer peripheral side of the rotor 14 toward the axis 22 side. However, the thickness of the heat insulating members 44 and 48 can be increased stepwise from the outer peripheral portion side of the rotor 14 toward the shaft center 22 side.

  Further, in the present embodiment, for example, as shown in FIG. 14, the diameter (cross-sectional area) of the supply-side flow path 34 can be set larger on the outer peripheral portion side of the rotor 14 than on the shaft center 22 side. . As a result, the contact area between the liquid refrigerant flowing in the supply-side flow path 34 and the rotor 14 is larger on the outer peripheral side of the rotor 14 than on the shaft 22 side. The amount of heat removed by the liquid refrigerant is larger on the outer peripheral portion side of the rotor 14 than on the shaft center 22 side. Similarly, for example, as shown in FIG. 14, the diameter (cross-sectional area) of the discharge side flow path 38 can be set larger on the outer peripheral side of the rotor 14 than on the axis 22 side. As a result, the contact area between the liquid refrigerant flowing in the discharge side flow path 38 and the rotor 14 is larger on the outer peripheral side of the rotor 14 than on the shaft center 22 side. The amount of heat removed by the liquid refrigerant is larger on the outer peripheral portion side of the rotor 14 than on the shaft center 22 side. FIG. 14 shows an example in which the cross-sectional area of the supply-side flow path 34 and the cross-sectional area of the discharge-side flow path 38 gradually increase from the axial center 22 side toward the outer peripheral portion side of the rotor 14.

  In the above description of the first embodiment, the heat removal flow path 36 for removing heat from the conductor 18 with the liquid refrigerant is formed in the iron core 16. However, in the present embodiment, for example, as shown in FIG. 15, the heat removal channel 36 can be formed inside the conductor 18. In that case, the conductor 18 is a tubular conductor extending from one end side to the other end side of the iron core 16 in the direction parallel to the axis 22, and the heat removal flow path 36 extends along the longitudinal direction of the tubular conductor 18. Let it be a flow path. In the example illustrated in FIG. 15, the supply-side flow path 34 is formed inside the short-circuit ring 20-1, and the heat removal of the short-circuit ring 20-1 is performed by the liquid refrigerant flowing through the supply-side flow path 34. Similarly, the discharge side flow path 38 is formed inside the short circuit ring 20-2, and the heat removal of the short circuit ring 20-2 is performed by the liquid refrigerant flowing through the discharge side flow path 38. Other configurations are the same as the example in which the heat removal channel 36 is formed in the iron core 16.

  Even when the heat removal flow path 36 is formed inside the conductor 18, the centrifugal force and rotation due to the rotation of the rotor 14 is suppressed while suppressing the reduction in efficiency of the rotating electrical machine, as in the case where the heat removal flow path 36 is formed in the iron core 16. By utilizing the liquid buoyancy due to heat received from the child 14, heat removal of the conductor 18 disposed on the outer peripheral portion of the rotor 14 can be efficiently performed. Furthermore, the transport power of the liquid refrigerant to the rotor 14 can be reduced. In addition, when forming the supply side flow path 34 and the discharge side flow path 38 in the short-circuit rings 20-1 and 20-2, the short-circuit rings 20-1 and 20-2 are joined to the shaft center 22, thereby Formation of the flow path 34 and the discharge side flow path 38 is facilitated.

  In the above description of the first embodiment, it is assumed that the rotating electrical machine is an induction machine and the conductor 18 is disposed on the outer peripheral portion of the rotor 14. However, in the present embodiment, for example, as shown in FIGS. 16 and 17, the rotating electrical machine is a synchronous machine, and a permanent magnet 58 is disposed on the outer periphery of the rotor 14 as a magnetic pole that generates a field flux. Good. In the example shown in FIGS. 16 and 17, a plurality of permanent magnets 58 are arranged along the circumferential direction of the rotor 14. Then, the rotating magnetic field generated by the winding 26 of the stator 12 and the field magnetic flux generated by the permanent magnet 58 of the rotor 14 interact to generate attraction and repulsion, thereby rotating the rotor 14 and obtaining magnet torque. . At that time, the rotor 14 generates heat, and in particular, the amount of heat generated at the outer peripheral portion where the permanent magnet 58 is disposed increases. Each permanent magnet 58 may be embedded in the rotor 14 (iron core 16), or may be exposed on the surface (outer peripheral surface) of the rotor 14.

  Even in the example in which the permanent magnet 58 is disposed, the heat removal flow path 36 is formed in the rotor 14 (iron core 16) and extends from one end side to the other end side of the iron core 16 in a direction parallel to the axis 22. It is a pipe-shaped flow path extending in a line. In the example in which the permanent magnets 58 are arranged, a plurality of heat removal flow paths 36 are arranged at intervals along the circumferential direction of the rotor 14, and each heat removal flow path 36 is connected to each permanent magnet 58. Each is formed in the vicinity. FIG. 17 shows an example in which the heat removal flow path 36 is formed on the radially inner side of the rotor 14 with respect to the permanent magnet 58. The liquid refrigerant supplied to each heat removal flow path 36 is carried away by removing heat from each permanent magnet 58 (and the surrounding iron core 16) located in the vicinity thereof, so that each permanent magnet 58 (and its surroundings) is removed. Heat removal of the iron core 16). Each heat removal channel 36 can be formed without being brought into contact with (in close proximity to) the permanent magnet 58, or can be formed in contact with the permanent magnet 58. Further, the heat removal flow path 36 may not necessarily be provided for each permanent magnet 58, and a plurality of heat removal flow paths 36 may be provided for each permanent magnet 58. Other configurations are the same as the example in which the conductor 18 is disposed on the outer peripheral portion of the rotor 14.

  Even when the permanent magnet 58 is disposed on the outer peripheral portion of the rotor 14, the rotor 14 is suppressed while suppressing a reduction in the efficiency of the rotating electrical machine, similarly to the case where the conductor 18 is disposed on the outer peripheral portion of the rotor 14. The permanent magnet 58 can be efficiently removed by utilizing the centrifugal force due to the rotation of and the liquid buoyancy due to the heat received from the rotor 14. Furthermore, the transport power of the liquid refrigerant to the rotor 14 can be reduced.

  Further, in the present embodiment, for example, as shown in FIG. 18, the supply-side flow path 34 can be formed to be inclined with respect to the radial direction of the rotor 14. In the example shown in FIG. 18, the supply-side flow path 34 is configured such that the end on the axis 22 side is on the outer side in the rotation axis direction of the rotor 14 than the end on the outer peripheral side of the rotor 14 (on one end side of the axis 22). ) To be located. Similarly, for example, as shown in FIG. 18, the discharge-side flow path 38 can be formed to be inclined with respect to the radial direction of the rotor 14. In the example shown in FIG. 18, the discharge-side flow path 38 has an end on the axis 22 side that is on the outer side of the rotor 14 in the rotation axis direction than the end on the outer peripheral side of the rotor 14 (the other end of the axis 22). It is inclined to be located on the side.

  In the present embodiment, for example, as shown in FIG. 19, both the refrigerant supply port 32 and the refrigerant discharge port 40 can be formed at one end (or the other end) of the shaft 22. In this case, the liquid refrigerant is supplied from one end (or the other end) of the shaft 22 and discharged from one end (or the other end) of the shaft 22.

  Further, in the present embodiment, for example, as shown in FIG. 20, the heat removal channel 36 is provided between one end (one end side) and the other end (the other end side) of the rotor 14 in the direction parallel to the axis 22. It is also possible to form a rectangular wave-like (wave-like) flow path that reciprocates. In this case, since the total length of the heat removal flow path 36 can be increased with respect to the total length of the supply side flow path 34 and the discharge side flow path 38, the liquid refrigerant in the supply side flow path 34 and the discharge side flow path 38. Compared with the amount of heat removed by, the amount of heat removed by the liquid refrigerant in the heat removal channel 36 can be increased. As a result, the pressure difference between the refrigerant discharge port 40 and the refrigerant supply port 32 can be further increased, and the transport power of the liquid refrigerant to the rotor 14 can be further reduced.

  18 to 20, the heat removal channel 36 may be formed in the iron core 16 or may be formed inside the conductor 18. And the conductor 18 may be arrange | positioned in the outer peripheral part of the rotor 14, and the permanent magnet 58 may be arrange | positioned.

“Embodiment 2”
21-23 is a figure which shows schematic structure of the rotary electric machine which concerns on Embodiment 2 of this invention, and shows the case where this invention is applied to an induction machine. 21 shows a schematic configuration of the rotor 14 as viewed from a direction orthogonal to the shaft center 22, FIG. 22 shows a cross-sectional view along AA in FIG. 21, and FIG. 23 shows a cross-sectional view along BB in FIG. In the following description of the second embodiment, the same or corresponding components as those in the first embodiment are denoted by the same reference numerals, and redundant descriptions are omitted.

  In the present embodiment, a heat removal flow path 136 communicating with the refrigerant supply port 32 and the refrigerant discharge port 40 is formed inside the rotor 14. The heat removal flow path 136 here is a pipe-shaped flow path extending from the shaft center 22 toward the outer peripheral portion of the rotor 14, and one end portion of the rotor 14 in the direction parallel to the shaft center 22 (short circuit ring 20-). 1) and the other end (short-circuit ring 20-2). As shown in FIGS. 22 and 23, in the short-circuit rings 20-1 and 20-2, a plurality of heat removal flow paths 136 extending along the radial direction of the rotor 14 are radial along the circumferential direction of the rotor 14. The heat removal flow paths 136 communicate with the refrigerant supply port 32 and the refrigerant discharge port 40 at the end portion on the shaft center 22 side. On the other hand, in each heat removal flow path 136, the end on the outer peripheral side of the rotor 14 is disposed in the vicinity of each conductor 18 (the end thereof) and is further closed. Each heat removal channel 136 can be formed by contacting the end of the outer peripheral portion of the rotor 14 with the end of the conductor 18 as shown in FIGS. 22 and 23, for example, as shown in FIG. As shown, the end on the outer peripheral side of the rotor 14 can be formed without being brought into contact with (close to) the end of the conductor 18. Further, the heat removal flow path 136 may not necessarily be provided for each conductor 18, and a plurality of heat removal flow paths 136 may be provided for each conductor 18. The number of heat removal flow paths 136 formed inside the rotor 14 can be arbitrarily set according to the number of conductors 18 and the thermal load of the conductors 18.

  The liquid refrigerant that has flowed into the rotor 14 from the refrigerant supply port 32 (one end portion of the shaft center 22) by a pump (not shown) is subjected to centrifugal force due to the rotation of the rotor 14, thereby It moves from the end on the core 22 side to the end on the rotor outer peripheral side. Since the temperature of the outer peripheral portion (conductor 18) of the rotor 14 becomes higher than that of the shaft center 22 due to heat generation, the liquid refrigerant that has moved to the end portion on the rotor outer peripheral portion side of each heat removal channel 136 is in the vicinity thereof. Heat is supplied from the respective conductors 18 (and the surrounding iron core 16). Due to the supply (heat reception) of this heat, a temperature change occurs in the liquid refrigerant in each heat removal flow path 136 and a density change occurs. Then, due to this density change, buoyancy (liquid buoyancy) is generated in the liquid refrigerant, so that a flow in each heat removal channel 136 is induced and convection occurs. Therefore, the liquid refrigerant that has moved to the end portion on the rotor outer peripheral portion side of each heat removal channel 136 flows back to the end portion on the shaft center 22 side by heat received from each conductor 18 as shown in FIG. Thus, heat can be removed from each conductor 18 (and the surrounding iron core 16) and carried away. In addition, about each conductor 18, in order to improve the heat mobility regarding a longitudinal direction, it is preferable to use the material excellent in thermal conductivity, such as aluminum and copper, for example.

  Thus, in this embodiment, each heat removal flow path 136 can be functioned as a thermosiphon, and the liquid refrigerant in each heat removal flow path 136 (within the thermosiphon) is transferred to the outer periphery of the rotor as the conductors 18 generate heat. The heat of each conductor 18 can be removed by moving heat from the end on the part side to the end on the axis 22 side. At that time, as in the first embodiment, since the components in the casing 24 such as the stator 12 are not exposed to the liquid refrigerant, the durability of the rotating electrical machine can be improved. Further, since the liquid refrigerant does not enter the gap between the rotor 14 and the stator 12, drag loss when the rotor 14 rotates with respect to the stator 12 can be reduced. And the heat removal of the outer peripheral part of the rotor 14 can be performed, without increasing the amount of magnetic gaps between the rotor 14 and the stator 12. Therefore, in this embodiment as well as in the first embodiment, the centrifugal force due to the rotation of the rotor 14 and the liquid buoyancy due to the heat received from the rotor 14 are utilized while suppressing the efficiency reduction of the rotating electrical machine. It is possible to efficiently remove heat from the conductor 18 disposed on the outer peripheral portion. Furthermore, in this embodiment, by forming the heat removal flow path 136 in a portion other than the iron core 16 (short-circuit rings 20-1 and 20-2), the influence of the heat removal flow path 136 on the magnetic characteristics of the rotor 14 is suppressed. be able to.

  In the present embodiment, for example, as shown in FIG. 26, the heat transfer channel 136 has a heat transfer member 50-1 that contacts the short-circuit ring 20-1 on the outer side in the rotation axis direction than the short-circuit ring 20-1 and the short-circuit ring 20. -2 may be formed on the heat transfer member 50-2 that contacts the short-circuit ring 20-2 on the outer side in the rotation axis direction than -2. In this case, the influence of the heat removal channel 136 on the magnetic characteristics of the rotor 14 can be further suppressed. Furthermore, the location where the heat removal flow path 136 is formed is not limited to the end portion of the rotor 14 in the direction parallel to the axis 22, and may be formed in the iron core 16, for example. In the present embodiment, the heat removal channel 136 may be formed with a slight inclination with respect to the radial direction of the rotor 14.

  In the description of Embodiment 2 above, the rotating electrical machine is an induction machine, and the conductor 18 is disposed on the outer peripheral portion of the rotor 14. However, also in this embodiment, as in the first embodiment, the rotating electrical machine may be a synchronous machine, and a permanent magnet (magnetic pole) 58 may be disposed on the outer peripheral portion of the rotor 14. In that case, the end (closed end) on the rotor outer peripheral side of the heat removal flow path 136 is disposed in the vicinity of (the end of) the permanent magnet 58. At that time, the end of the heat removal flow path 136 on the outer peripheral side of the rotor can be not brought into contact (close to) the permanent magnet 58, or can be brought into contact with the end of the permanent magnet 58. The iron core 16 is preferably formed of a powder magnetic core material having a three-dimensional orientation in order to improve heat mobility in a direction parallel to the axis 22. The dust core material here is a material obtained by compacting a powder coated with a film that does not conduct electricity on the surface of fine particles of ferromagnetic material such as iron.

  Even in the example in which the permanent magnet 58 is provided, the heat removal flow path 136 can function as a thermosiphon in the same manner as in the example in which the conductor 18 is provided, and in the heat removal flow path 136 as the permanent magnet 58 generates heat. The heat of the permanent magnet 58 can be removed by moving the liquid refrigerant from the end on the rotor outer peripheral side to the end on the axis 22 side. As a result, the permanent magnet 58 disposed on the outer peripheral portion of the rotor 14 is utilized by utilizing the centrifugal force due to the rotation of the rotor 14 and the liquid buoyancy due to the heat received from the rotor 14 while suppressing the reduction in efficiency of the rotating electrical machine. Heat removal can be performed efficiently.

  In the present embodiment, similarly to the first embodiment, both the refrigerant supply port 32 and the refrigerant discharge port 40 may be formed at one end (or the other end) of the shaft 22.

  As mentioned above, although the form for implementing this invention was demonstrated, this invention is not limited to such embodiment at all, and it can implement with a various form in the range which does not deviate from the summary of this invention. Of course.

It is a figure which shows schematic structure of the rotary electric machine which concerns on Embodiment 1 of this invention. It is a figure which shows schematic structure of the rotary electric machine which concerns on Embodiment 1 of this invention. It is a figure which shows schematic structure of the rotary electric machine which concerns on Embodiment 1 of this invention. It is a figure which shows schematic structure of the rotary electric machine which concerns on Embodiment 1 of this invention. It is a figure which shows schematic structure of the rotary electric machine which concerns on Embodiment 1 of this invention. It is a figure which shows the other schematic structure of the rotary electric machine which concerns on Embodiment 1 of this invention. It is a figure showing the emitted-heat amount distribution in a supply side flow path, a heat removal flow path, and a discharge side flow path. It is a figure which shows the pressure change of a refrigerant | coolant supply port when changing the emitted-heat amount distribution in a supply side flow path, a heat removal flow path, and a discharge side flow path. It is a figure which shows the other schematic structure of the rotary electric machine which concerns on Embodiment 1 of this invention. It is a figure which shows the other schematic structure of the rotary electric machine which concerns on Embodiment 1 of this invention. It is a figure showing the emitted-heat amount distribution in a supply side flow path, a heat removal flow path, and a discharge side flow path. It is a figure showing the emitted-heat amount distribution in a supply side flow path, a heat removal flow path, and a discharge side flow path. It is a figure showing the emitted-heat amount distribution in a supply side flow path, a heat removal flow path, and a discharge side flow path. It is a figure showing the emitted-heat amount distribution in a supply side flow path, a heat removal flow path, and a discharge side flow path. It is a figure which shows the pressure change of a refrigerant | coolant supply port when the calorific value distribution in a supply side flow path and the calorific value distribution in a discharge side flow path are each changed. It is a figure which shows the other schematic structure of the rotary electric machine which concerns on Embodiment 1 of this invention. It is a figure which shows the other schematic structure of the rotary electric machine which concerns on Embodiment 1 of this invention. It is a figure which shows the other schematic structure of the rotary electric machine which concerns on Embodiment 1 of this invention. It is a figure which shows the other schematic structure of the rotary electric machine which concerns on Embodiment 1 of this invention. It is a figure which shows the other schematic structure of the rotary electric machine which concerns on Embodiment 1 of this invention. It is a figure which shows the other schematic structure of the rotary electric machine which concerns on Embodiment 1 of this invention. It is a figure which shows the other schematic structure of the rotary electric machine which concerns on Embodiment 1 of this invention. It is a figure which shows the other schematic structure of the rotary electric machine which concerns on Embodiment 1 of this invention. It is a figure which shows schematic structure of the rotary electric machine which concerns on Embodiment 2 of this invention. It is a figure which shows schematic structure of the rotary electric machine which concerns on Embodiment 2 of this invention. It is a figure which shows schematic structure of the rotary electric machine which concerns on Embodiment 2 of this invention. It is a figure which shows the other schematic structure of the rotary electric machine which concerns on Embodiment 2 of this invention. It is a figure explaining the flow of the liquid refrigerant | coolant in the heat removal flow path in Embodiment 2 of this invention. It is a figure which shows the other schematic structure of the rotary electric machine which concerns on Embodiment 2 of this invention.

Explanation of symbols

  12 Stator, 14 Rotor, 16 Iron core, 18 Conductor, 20-1, 20-2 Short circuit ring, 22 Shaft center, 24 Casing, 26 Winding, 32 Refrigerant supply port, 34 Supply side flow path, 36, 136 Heat flow path, 38 discharge side flow path, 40 refrigerant discharge port, 44, 48 heat insulation member, 58 permanent magnet.

Claims (14)

A rotor in which conductors or magnetic poles are disposed on the outer peripheral portion of the iron core, the rotor having an axis disposed along the rotation center axis;
A stator disposed opposite the outer periphery of the iron core;
A rotating electric machine comprising:
A refrigerant supply port for supplying liquid refrigerant into the rotor is formed at one end of the shaft,
A heat removal flow path is formed in the iron core for removing heat from a conductor or a magnetic pole disposed on the outer peripheral portion of the iron core by the liquid refrigerant supplied from the refrigerant supply port.
A rotating electrical machine in which a refrigerant discharge port that communicates with a heat removal flow path and discharges liquid refrigerant supplied to the heat removal flow path from the inside of the rotor is formed at one end or the other end of the shaft. The rotating electrical machine according to claim 1,
The heat removal flow path is a rotating electrical machine including a pipe-shaped flow path extending from one end side to the other end side of the iron core in a direction parallel to the axis. The rotating electrical machine according to claim 1 or 2,
A flow path extending from the shaft center toward the outer periphery of the rotor, the end on the shaft center side communicating with the refrigerant supply port, and the end on the outer periphery side of the rotor communicating with one end of the heat removal flow path A supply-side flow path is formed inside the rotor,
A flow path extending from the shaft center toward the outer peripheral portion of the rotor, wherein the end portion on the shaft center side communicates with the refrigerant discharge port, and the end portion on the outer peripheral portion side of the rotor is connected to the other end portion of the heat removal flow path A rotating electrical machine in which a discharge-side flow path that communicates is formed inside a rotor. The rotating electrical machine according to claim 3,
The contact area between the liquid refrigerant flowing through the heat removal flow path and the rotor is at least of the contact area between the liquid refrigerant flowing through the supply side flow path and the rotor, and the contact area between the liquid refrigerant flowing through the discharge side flow path and the rotor. A rotating electrical machine larger than one. The rotating electrical machine according to claim 3 or 4,
At least one of the contact area between the liquid refrigerant flowing through the supply-side flow path and the rotor and the contact area between the liquid refrigerant flowing through the discharge-side flow path and the rotor is closer to the outer peripheral side of the rotor than the shaft center side. A large rotating electric machine. The rotating electrical machine according to any one of claims 3 to 5,
A rotating electrical machine in which a heat insulating member is disposed around at least one of a supply side flow path and a discharge side flow path. The rotating electrical machine according to claim 6,
The rotating electric machine is such that the heat insulating member is thicker on the axial side than on the outer peripheral side of the rotor. The rotating electrical machine according to any one of claims 3 to 7,
The supply side flow path is formed at one end of the rotor in a direction parallel to the axis,
The discharge-side flow path is a rotating electrical machine formed at the other end of the rotor in a direction parallel to the axis. The rotating electrical machine according to any one of claims 3 to 8,
A plurality of supply-side flow paths are formed radially and a plurality of discharge-side flow paths are formed radially,
A rotating electrical machine in which a plurality of heat removal channels are arranged in the circumferential direction of the rotor. A rotor having a conductor disposed on the outer periphery thereof, the rotor having an axis disposed along the rotation center axis thereof;
A stator disposed opposite to the outer periphery of the rotor;
A rotating electric machine comprising:
A refrigerant supply port for supplying liquid refrigerant into the rotor is formed at one end of the shaft,
A heat removal flow path is formed inside the conductor to communicate with the refrigerant supply port, and to remove heat from the conductor disposed on the outer peripheral portion of the rotor by the liquid refrigerant supplied from the refrigerant supply port.
A rotating electrical machine in which a refrigerant discharge port that communicates with a heat removal flow path and discharges liquid refrigerant supplied to the heat removal flow path from the inside of the rotor is formed at one end or the other end of the shaft. The rotating electric machine according to claim 10,
The conductor disposed on the outer periphery of the rotor is a tubular conductor extending from one end side of the rotor toward the other end side in the direction parallel to the axis,
The heat removal flow path includes a flow path extending along a longitudinal direction of the tubular conductor. A rotor in which a conductor or a magnetic pole is disposed on an outer peripheral portion, and a rotor in which an axis is disposed along the rotation center axis;
A stator disposed opposite to the outer periphery of the rotor;
A rotating electric machine comprising:
A refrigerant supply port for supplying liquid refrigerant into the rotor is formed at one end of the shaft,
A refrigerant outlet for discharging liquid refrigerant from the inside of the rotor is formed at one end or the other end of the shaft,
A pipe-shaped flow path extending from the shaft center toward the outer peripheral portion of the rotor, the end portion on the shaft center side communicating with the refrigerant supply port and the refrigerant discharge port, and the end portion on the outer peripheral portion side of the rotor A closed heat removal flow path is formed inside the rotor,
In the heat removal flow path, the liquid refrigerant moves heat from the end portion on the outer peripheral portion side of the rotor to the end portion on the axial center side along with the heat generation of the conductor or magnetic pole disposed on the outer peripheral portion of the rotor, A rotating electrical machine that is a flow path for removing heat from a conductor or magnetic pole disposed on an outer peripheral portion of a rotor. The rotating electrical machine according to claim 12,
The heat removal flow path is a rotating electrical machine formed at the end of the rotor in a direction parallel to the axis. The rotating electrical machine according to claim 12 or 13,
A rotating electrical machine in which a plurality of heat removal channels are formed radially.

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