JP2012235546A - Rotor and rotating electric machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rotor for a rotating electric machine which enables the rotor having heat generation distribution in the circumferential direction to be cooled efficiently.SOLUTION: A rotor 12 includes a rotating shaft 18 and a rotor core 40. The rotor core 40 includes: first hole portions 50 each formed in a region where heat generation amount during rotating operation is relatively large; and a second hole portion 52 formed in a region where the heat generation amount is relatively small. A refrigerant storage portion 44 for receiving a refrigerant via a shaft portion 20 of the rotating shaft 18 is installed on the axial end outer side of the rotor core 40 so as to be adjacent to respective openings of the first hole portions 50 and the second hole portion 52. A flow control member 36 is disposed between the refrigerant storage portion 44 and the respective openings of the first hole portions 50 and the second hole portion 52. First refrigerant passages communicated with the openings of the first hole portions 50 and a second refrigerant passage communicated with the second hole portion 52 are formed in the flow control member 36. An opening area of the first refrigerant passage is set larger than that of the second refrigerant passage.

Description

  The present invention relates to a rotor and a rotating electrical machine, and more particularly, to a rotor and a rotating electrical machine including a rotor core in which a refrigerant passage is formed.

  Conventionally, a rotor in which a coolant passage through which a cooling medium flows is formed in a rotor core configured by laminating electromagnetic steel sheets, and a rotating electrical machine using the rotor are known.

  For example, a rotor core of a permanent magnet type synchronous rotating electrical machine disclosed in Japanese Patent Application Laid-Open No. 2009-55737 (Patent Document 1) is configured by alternately laminating first and second electromagnetic steel plates, and the first and second electromagnetics. The steel plate has holes that form the refrigerant passages, and the holes are shifted from each other in the circumferential direction to form a refrigerant passage that communicates over the entire circumference. It is described that the cooling performance is improved by supplying evenly in all directions.

JP 2009-55737 A

  When the rotating electric machine actually rotates, the rotor may have a heat generation distribution in the circumferential direction. In that case, in the structure in which the cooling medium is uniformly supplied and uniformly cooled in the entire circumferential direction of the rotor as in Patent Document 1, the rotor having the heat distribution in the circumferential direction as described above is efficiently cooled. I can't.

  An object of the present invention is to provide a rotor and a rotating electrical machine that can efficiently cool a rotor having a heat generation distribution in the circumferential direction.

  The rotor according to the present invention is a rotor including a rotating shaft and a rotor core fixed to the outer periphery thereof, and the rotor core is formed to extend in the axial direction in a region where the amount of heat generated during the rotation operation is relatively large. A first hole and a second hole formed to extend in the axial direction in a region where the heat generation amount is relatively small, and on the outer side of the axial end of the rotor core via the shaft of the rotating shaft. A refrigerant reservoir that receives the cooling medium is provided adjacent to each opening of the first hole and the second hole, and between the refrigerant reservoir and each opening of the first hole and the second hole. A flow rate adjusting member is disposed in the first flow rate adjusting member, and a first refrigerant passage communicating with the opening of the first hole portion and a second refrigerant passage communicating with the second hole portion are formed in the flow rate adjusting member. The opening area of the passage is larger than the opening area of the second refrigerant passage It is set.

  In the rotor according to the present invention, a permanent magnet may be embedded in the rotor core, and the first hole portion may be formed in contact with the permanent magnet.

  Further, in the rotor according to the present invention, the pair of permanent magnets constitutes one magnetic pole, the pair of permanent magnets are arranged apart from each other in the circumferential direction, and the first hole portion is a radial direction of the pair of permanent magnets. Two each may be formed in contact with the inner end, and the second hole may be formed between the two first holes.

  In the rotor according to the present invention, when the permanent magnet is included in the magnetic pole of the rotor core, the first and second holes may constitute a flux barrier against the magnetic flux from the permanent magnet.

  Further, in the rotor according to the present invention, the rotating shaft has a flange portion that protrudes radially outward from an outer peripheral surface thereof and has a concave portion formed on a surface facing the rotor core, and the refrigerant storage portion is You may form by the space divided by the said recessed part and the said flow volume adjustment member.

  The rotor according to the present invention may further include an end plate disposed outside the axial end portion of the rotor core, and the end plate has a recess formed on a surface facing the rotor core, and the refrigerant storage portion May be formed by a space defined by the recess and the flow rate adjusting member.

  In the rotor according to the present invention, the flow rate adjustment member is configured by an annular plate disposed between the rotor core and the refrigerant reservoir, and the first and second refrigerant passages are included in the flow rate adjustment member. It consists of a notch part formed in the peripheral part, and the width | variety of the notch part of the said 1st refrigerant path may be set wider than the width | variety of the said 2nd refrigerant path.

  Furthermore, in the rotor according to the present invention, the rotor core may be a plate-shaped member laminate, and the annular plate may be formed by a part of the plate-shaped member.

  And the rotary electric machine which concerns on this invention is equipped with the rotor which consists of one of the said structures, and the stator arrange | positioned on a rotor outer periphery.

  According to the rotor and the rotating electrical machine according to the present invention, the first hole formed in the region where the heat generation amount is relatively large during the rotation operation is more from the refrigerant reservoir through the first refrigerant passage having a large opening area. The cooling medium can be supplied. Therefore, the cooling performance by the cooling medium can be set according to the circumferential heat generation distribution in the rotor, and the rotor can be efficiently cooled. As a result, it is possible to maintain or improve the output characteristics of the rotating electrical machine by reducing the rotor temperature.

1 is an axial cross-sectional view of a rotating electrical machine that is a first embodiment of the present invention. It is the sectional view on the AA line in FIG. FIG. 3 is an enlarged view of a one-dot chain line region B in FIG. 2. It is an axial sectional view of the rotating electrical machine according to the second embodiment of the present invention. It is an axial sectional view of the rotating electrical machine according to the third embodiment of the present invention.

  DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments according to the present invention (hereinafter referred to as embodiments) will be described in detail with reference to the accompanying drawings. In this description, specific shapes, materials, numerical values, directions, and the like are examples for facilitating the understanding of the present invention, and can be appropriately changed according to the application, purpose, specification, and the like. In addition, when a plurality of embodiments are included in the following, it is assumed in advance that the configurations of the embodiments are used in any combination.

(First embodiment)
1 is an axial sectional view of the rotating electrical machine 10 of the first embodiment, FIG. 2 is a sectional view taken along the line AA in FIG. 1, and FIG. 3 is an enlarged view of a one-dot chain line region B in FIG. is there. The rotating electrical machine 10 includes a rotor 12 and a stator 14. The rotor 12 and the stator 14 are accommodated in a cylindrical case 16 whose both axial ends are closed.

  Referring to FIG. 1, the stator 14 includes a cylindrical stator core 15a and a stator coil 15b wound around the stator core 15a. The stator core 15a is configured by laminating a number of electromagnetic steel plates punched into an annular shape. The outer peripheral surface of the stator core 15 a is fixed on the inner peripheral surface of the case 16. Further, the stator core 15a has a plurality of teeth on the inner peripheral portion thereof. The teeth protrude radially inward and are arranged at equal intervals in the circumferential direction.

  A slot is formed between adjacent teeth. The slot is formed as a groove extending over the entire axial direction of the stator core 15a. The stator coil 15b is wound around the teeth and has a slot inner portion located in the slot and a coil end portion bulging outward from the axial end surface of the stator core 15a.

  The rotor 12 is disposed inside the stator 14 via an air gap. The rotor 12 includes a rotating shaft 18 and a rotor core 40. The rotary shaft 18 includes a shaft portion 20 having a hollow and substantially cylindrical shape, and a substantially disk-shaped flange portion 22 that protrudes radially outward from the outer periphery of the shaft portion 20. Both axial ends of the shaft portion 20 of the rotating shaft 18 are rotatably supported by bearing members 24 fixed to the end wall 17 of the case 16. A cooling medium passage 26 is formed in the shaft portion 20 of the rotating shaft 18 so as to extend in the axial direction.

  Oil as a cooling medium is collected at the bottom of the case 16. The amount of oil is set so that the height of the oil surface C is lower than the outer peripheral surface of the rotor core 40, and does not become the rotational resistance of the rotor 12. The end wall 17 of the case 16 is formed with an oil suction hole portion 17 a for sucking out oil accumulated at the bottom of the case 16.

  One end of an oil pipe 28 provided with a pump 30 is connected to the oil suction hole 17 a of the end wall 17 of the case 16. On the other hand, the other end portion of the oil pipe 28 is connected to the cooling medium passage 26 at the end portion of the shaft portion 20 of the rotating shaft 18 exposed to the outside of the case 16. Thus, by operating the pump 30, the oil accumulated at the bottom of the case 16 can be sucked and supplied to the cooling medium passage 26 in the rotary shaft 18.

  The oil pipe 28 may be provided with an oil cooler for promoting heat dissipation from the oil to lower the temperature. Further, in the present embodiment, the cooling medium passage 26 in the shaft portion 20 of the rotating shaft 18 is shown as penetrating in the axial direction, but the present invention is not limited to this, and the cooling medium passage 26 is the flange portion. You may close in the edge part by 22 side.

  The rotor core 40 is formed by stacking punched disk-shaped electromagnetic steel plates in the axial direction. A shaft insertion hole 42 through which the shaft portion 20 of the rotary shaft 18 is inserted is formed in the center of the substantially cylindrical rotor core 40 so as to penetrate in the axial direction.

  The rotor 12 further includes an end plate 32 having a substantially disk shape. The end plate 32 is preferably formed of a nonmagnetic material such as aluminum, copper, stainless steel, or resin so as not to affect the magnetic characteristics of the rotor core 40.

  The rotor 12 is assembled as follows. First, a flow rate adjusting member 36 described later is mounted on the shaft portion 20 of the rotating shaft 18 from the direction of arrow D. Subsequently, the rotor core 40 is externally mounted on the shaft portion 20, and the flow rate adjusting member 36 is sandwiched between the axial end surface of the rotor core 40 and the flange portion 22. Then, the end plate 32 is mounted on the shaft portion 20 of the rotary shaft 18 and pressed against the other axial end surface of the rotor core 40 with a predetermined pressing force. In this state, the cylindrical caulking member 38 sheathed on the shaft portion 20 is caulked and fixed, whereby the rotor core 40 is fixed to the rotating shaft 18 with its axial position determined. In addition, the circumferential position of the rotor core 40 with respect to the rotating shaft 18 is also determined by a method such as concave-convex fitting with the shaft portion 20 of the rotating shaft 18 or press fitting onto the shaft portion 20.

  On the surface of the flange portion 22 of the rotating shaft 18 that faces the rotor core 40, an annular recess 23 is formed surrounding the shaft portion 20. The recess 23 formed in the flange portion 22 of the rotating shaft 18 has a circumferential wall surface and a radial wall surface.

  Further, the shaft portion 20 of the rotary shaft 18 is formed with an oil discharge hole 27 communicating with the cooling medium passage 26 at a position corresponding to the concave portion 23. A plurality of oil discharge holes 27 (four in this embodiment, see FIG. 2) are formed in a uniform arrangement in the circumferential direction.

  The flow rate adjusting member 36 is configured by an annular plate having substantially the same outer diameter as the rotor core 40 and the flange portion 22. The inner peripheral edge of the flow rate adjusting member 36 is located so as to protrude radially inward from the circumferential wall surface of the recess 23 of the flange portion 22. Similarly to the end plate 32, the flow rate adjusting member 36 is also preferably formed of a nonmagnetic material such as aluminum, copper, stainless steel, or resin so as not to affect the magnetic characteristics of the rotor core 40.

  An annular space defined by the circumferential wall surface and radial wall surface in the recess 23 of the flange portion 22 and the flow rate adjusting member 36 is used as the refrigerant storage portion 44. Since the refrigerant reservoir 44 is opened inward in the radial direction, the oil discharged from the oil discharge hole 27 formed in the shaft portion 20 of the rotary shaft 18 can be received.

  In the present embodiment, the refrigerant reservoir 44 is formed by a space that opens radially inward, but is not limited to this, and the refrigerant reservoir is closed by the inner peripheral side wall surface of the recess. It is good also as a part. In this case, a groove-like oil supply path that connects the oil discharge hole and the refrigerant reservoir to the rotor facing surface of the flange 22 may be formed.

  Referring to FIG. 2, the rotor core 40 is a permanent magnet embedded rotor including a plurality of magnetic poles 46 on the outer peripheral portion. In the present embodiment, eight magnetic poles 46 are provided in the circumferential direction in an equal arrangement.

  A pair of permanent magnets 48 is disposed on each magnetic pole 46. The permanent magnet 48 has a flat rectangular end face and a cross section, and extends over the entire axial direction of the rotor core 40. The permanent magnet 48 is inserted and fixed in a magnet insertion hole formed in the rotor core 40 so as to extend in the axial direction. The pair of permanent magnets 48 included in the magnetic pole 46 are provided away from each other in the circumferential direction, and are arranged in a substantially V shape so that the distance between them increases outward in the radial direction.

  A first hole 50 and a second hole 52 are formed extending in the axial direction inside the rotor core 40 and radially inward of the magnetic poles 46. The first hole 50 is provided at a position in contact with the inner peripheral side end of the pair of permanent magnets 48, and two first holes 50 are formed in the present embodiment. The second hole portion 52 is provided with a bridge portion 54 sandwiched between the two first hole portions 50, and is formed to extend radially inward from the first hole portion 50 in the present embodiment. Has been. These first and second holes 50 and 52 constitute a flux barrier that restricts the flow of magnetic flux generated from the permanent magnet 48 (and / or magnetic flux that flows from the stator to the magnetic pole of the rotor) to define a magnetic path. At the same time, it also functions as an oil passage as will be described later.

  The first hole 50 is provided in a region in the rotor core 40 where the amount of heat generated during rotation is relatively large. Specifically, when the rotor 12 rotates at a particularly high speed by energizing the stator coil 15b and forming a rotating magnetic field in the stator 14, the loss in the permanent magnet 48 increases and heat is generated. The permanent magnet 48 may be demagnetized when the temperature rises due to heat generation. When the magnetic force of the permanent magnet decreases due to demagnetization, the performance as a rotating electric machine cannot be exhibited, and the power performance decreases. Therefore, in the present embodiment, as will be described later, the first hole 50 is formed at a position in contact with the permanent magnet 48 in order to increase the cooling performance with respect to the permanent magnet 48 that is greatly affected by heat generation in the rotor core 40.

  On the other hand, the second hole 52 in the rotor 12 of the present embodiment is arranged away from the permanent magnet 48 that generates a large amount of heat during high-speed rotation operation. That is, it can be said that the second hole portion 52 is provided in a region where the amount of heat generated during the rotation operation in the rotor core 40 is relatively small. However, since the second hole portion 52 is formed facing the magnetic path region located between the two first hole portions 50 and sandwiched between the pair of permanent magnets 48, the second hole 52 will be described later. The magnetic path region formed of the laminated steel plate included in the magnetic pole 46 can be effectively cooled by the oil supplied to the part 50, and thereby the core iron loss can be suppressed.

  Referring to FIG. 3, the first and second holes 50 and 52 are open at positions adjacent to the refrigerant reservoir 44 formed outside the axial end of the rotor core 40. The flow rate adjusting member 36 includes a first refrigerant passage 56 that communicates with the two first holes 50 and a second refrigerant passage 58 that communicates with the second hole 52.

  The first and second refrigerant passages 56 and 58 are formed by cut portions that enter a rectangular shape from the inner peripheral edge of the flow rate adjusting member 36 formed of an annular plate toward the radially outer side. Each notch part which makes the 1st and 2nd refrigerant passages 56 and 58 is formed in the same depth about a diameter direction. That is, the radially outer bottoms of the first and second refrigerant passages 56 and 58 are positioned so as to be aligned on the same radius R1 from the rotation center of the rotor core 40 (see FIG. 2). On the other hand, when the widths da and dc of the first refrigerant passage 56 and the width db of the second refrigerant passage 58 in directions substantially along the circumferential direction are set, da = dc> db is satisfied. Thereby, the opening area of the first refrigerant passage 56 communicating with the first hole 50 is set larger than the opening area of the second refrigerant passage 58 communicating with the second hole 52.

  The first refrigerant passage 56 communicates with the first hole 50 at a part of the cutout portion on the radially outer side. On the other hand, the second refrigerant passage 58 is formed in a position and shape where the entire cut portion communicates with the second hole 52. The oil discharged radially outward from the oil discharge hole 27 of the shaft portion 20 of the rotary shaft 18 is received and stored in the refrigerant storage portion 44, but is stored in the refrigerant storage portion 44 by centrifugal force due to the rotation operation of the rotor 12. The oil is held in an annular shape on the circumferential wall surface of the recess 23 corresponding to the bottom 45 of the refrigerant reservoir 44. Then, as the amount of oil in the refrigerant reservoir 44 increases, the oil level C moves radially inward (in the direction of arrow E in FIG. 3), and the oil level C is in the first and second refrigerant paths 56. , 58, oil is supplied from the refrigerant reservoir 44 to the first and second holes 50, 52 via the refrigerant passages 56, 58. At this time, as described above, the opening area of the first refrigerant passage 56 is set larger than the opening area of the second refrigerant passage 58, so that the amount of oil supplied to the first hole 50 is the second hole 52. As a result, the cooling performance in the first hole 50 is larger than the cooling performance in the second hole 52.

  In the present embodiment, the first and second refrigerant passages 56 and 58 are formed by the cut portions opened at the inner peripheral edge of the flow rate adjusting member 36 made of an annular plate. However, the present invention is not limited to this. You may form by the through-hole of rectangular shape or ellipse shape etc. which were formed in the plate. In this case, what is necessary is just to set the opening area of a 1st and 2nd refrigerant path as mentioned above by varying the magnitude | size of a through-hole.

  Referring to FIG. 1, a plurality of oil discharge holes 33 are formed in the end plate 32. The oil discharge hole 33 is formed to face the opening of the second hole 52 at the other axial end of the rotor core 40. Since a space is formed between the other axial end of the rotor core 40 and the oil discharge hole 33 of the end plate 32, the oil that has flowed out of the rotor core 40 through the first hole 50 also passes through the space. It can be discharged from the oil discharge hole 33 to the outside of the rotor.

  Next, the cooling operation in the rotating electrical machine 10 having the above configuration will be described.

  When the pump 30 is operated in the rotating electrical machine 10 in which the rotor 12 rotates, the oil accumulated at the bottom of the case 16 is sucked by the one end of the oil pipe 28 from the oil suction hole 17a, and the other end of the oil pipe 28 is From the end of the rotary shaft 18 to the cooling medium passage 26.

  The oil supplied to the cooling medium passage 26 flows to the one side in the axial direction of the cooling medium passage 26 in the shaft portion 20 of the rotary shaft 18 and reaches a portion communicating with the oil discharge hole 27. Then, the oil is discharged radially outward from the oil discharge hole 27 by the centrifugal force generated by the rotating rotor 12.

  The oil discharged from the oil discharge hole 27 is received and stored by the refrigerant storage unit 44. The oil stored in the refrigerant reservoir 44 is held in an annular shape while being pressed against the bottom of the refrigerant reservoir 44 by the centrifugal force generated by the rotating rotor 12.

  The amount of oil stored in the refrigerant storage unit 44 increases, and the oil level C moves radially inward (arrow E direction). When the oil level C reaches the end in the cut direction of the first and second refrigerant passages 56, 58, the oil passes through the first and second refrigerant passages 56, 58 and the first in the rotor core 40. And supplied to the second holes 50 and 52. At this time, since the opening area of the first refrigerant passage 56 is formed larger than the opening area of the second refrigerant passage 58, the amount of oil supplied to the first hole 50 is the amount of oil supplied to the second hole 52. It is adjusted to be larger than the amount.

  The oil supplied from the refrigerant reservoir 44 to the first and second holes 50 and 52 in the rotor core 40 via the first and second refrigerant passages 56 and 58 is caused by the centrifugal force generated by the rotating rotor 12 and the outer peripheral side wall surface. It flows to the other side in the axial direction while being pressed against. At this time, since the inner peripheral side end of the permanent magnet 48 is exposed in the first hole 50, the permanent magnet 48 is directly and effectively applied by the oil flowing in the first hole 50 in a relatively large amount. To be cooled. On the other hand, a relatively small amount of oil flowing in the second hole 52 flows along the inner peripheral side portion of the magnetic path region included in the magnetic pole 46 of the rotor core 40, so that the magnet positioned between the pair of permanent magnets 48. The road area can be effectively cooled.

  Oil that flows through the first and second holes 50 and 52 of the rotor core 40 and reaches the axial end of the rotor core 40 is discharged from the oil discharge holes 33 of the end plate 32 to the outside of the rotor. The oil discharged to the outside of the rotor accumulates at the bottom in the case 16 due to the gravitational action. Then, the oil is circulated and supplied from the oil suction hole 17 a to the rotary shaft 18 through the oil pipe 28 by suction by the pump 30.

  As described above, according to the rotor 12 of the present embodiment and the rotary electric machine 10 including the same, the opening area is formed in the first hole 50 formed in the rotor core 40 in the region where the heat generation amount is relatively large during the rotation operation. More cooling medium can be supplied from the refrigerant reservoir 44 via the large first refrigerant passage 56. Therefore, the cooling performance by oil can be set according to the heat generation distribution in the circumferential direction in the rotor 12, and the rotor 12 can be efficiently cooled. As a result, the output characteristics of the rotating electrical machine 10 can be maintained or improved by reducing the rotor temperature.

  More specifically, the rotor 12 of the present embodiment is a permanent magnet embedded rotor, and the first hole 50 is formed in contact with a pair of permanent magnets 48 constituting the magnetic pole 46. Therefore, the permanent magnet 48 can be directly and effectively cooled by the oil flowing along the first hole 50, and the output performance is effectively reduced due to the demagnetization of the permanent magnet 48 due to heat generation. Can be prevented.

  Further, in the rotor 12 of the present embodiment, the second hole 52 is formed in the inner peripheral side portion of the magnetic path region between the pair of permanent magnets 48 in the magnetic pole 46, and therefore flows in the second hole 52. The magnetic path region can be effectively cooled by the oil. Thereby, the core loss in the magnetic pole 46 of the rotor core 40 can be reduced, and this can also contribute to the improvement of the output performance of the rotating electrical machine 10.

  Further, in the rotor 12 of the present embodiment, the first and second holes 50 and 52 are the flux barriers in the magnetic pole 46 because the first and second holes 50 and 52 serving as the refrigerant passages in the rotor core 40 constitute a flux barrier. As compared with the case where the magnetic flux is formed separately from the flux barrier of the magnetic pole 46, the decrease in the centrifugal strength of the rotor core 40 can be suppressed.

  Moreover, in the rotor 12 of this embodiment, since the refrigerant | coolant storage part 44 provided in the axial direction edge part outer side of the rotor core 40 is formed by the recessed part 23 of the flange part 22 of the rotating shaft 18, it is for forming a refrigerant | coolant storage part. There is no need to provide a special member separately, and there is an advantage that the configuration can be simplified.

  In the present embodiment, the permanent magnet 48 is exposed to the first hole 50 and directly cooled by oil. However, the present invention is not limited to this, and the first hole is close to the permanent magnet. And may be configured to cool through a narrow steel plate lamination region.

(Second Embodiment)
Next, with reference to FIG. 4, the rotor 12 and the rotary electric machine 10 of 2nd Embodiment are demonstrated.

  In the rotor 12 of the rotating electrical machine 10 of the second embodiment, an end plate 60 is provided instead of the flange portion 22 in the first embodiment. A recess 23 is formed on the rotor facing surface of the end plate 60. Further, the end plate 60 is in contact with the contact portion 21 of the rotary shaft 18 and the axial position with respect to the shaft portion 20 is determined. The end plate 60 is also preferably formed of a nonmagnetic material such as aluminum, copper, stainless steel, or resin so as not to affect the magnetic characteristics of the rotor core 40. Since other configurations are the same as those in the first embodiment, the same or corresponding components are denoted by the same or corresponding reference numerals, and redundant description is omitted with the aid of the description.

  According to the rotor 12 and the rotary electric machine 10 of 2nd Embodiment, there can exist an effect substantially the same as the said 1st Embodiment. Moreover, in this embodiment, since the refrigerant | coolant storage part 44 is formed with the end plate 60, the diameter of the rotating shaft 18 can be reduced and, thereby, the specific effect that the manufacturing cost of the rotating shaft 18 can be reduced significantly. Can play.

(Third embodiment)
Next, with reference to FIG. 5, the rotor 12 and the rotary electric machine 10 of 3rd Embodiment are demonstrated.

  The rotor 12 and the rotating electrical machine 10 of the third embodiment have substantially the same configuration as that of the first embodiment. The difference is that instead of the flow rate adjusting member 36 in the first embodiment, one or more (two in the present embodiment) electromagnetic steel plates laminated in the axial direction end of the rotor core 40 are used for oil. It is the point which fulfill | performed the flow volume adjustment function. Since other configurations are the same as those in the first embodiment, the same or corresponding components are denoted by the same or corresponding reference numerals, and redundant description is omitted with the aid of the description.

  According to the rotor 12 and the rotary electric machine 10 of 3rd Embodiment, there can exist an effect substantially the same as the said 1st Embodiment. Further, in the present embodiment, the oil flow rate adjusting unit is formed by the electromagnetic steel plate that is a plate-like member constituting the rotor core 40, so that the oil flow rate adjusting unit can be incorporated integrally when the rotor core 40 is laminated. Assembling becomes easy, and since the flow rate adjusting member does not exist as a separate member, it is possible to achieve a specific effect that the cost can be reduced rather than the number of parts.

  In addition, although 1st thru | or 3rd embodiment was demonstrated above, the rotor and rotary electric machine which concern on this invention are not limited to said structure, A various change or improvement is possible.

  Although the rotor 12 of each of the above embodiments has been described as including a pair of permanent magnets 48 in one magnetic pole 46, the number of permanent magnets included in each magnetic pole may be one or three or more.

  In each of the above embodiments, the rotor 12 is described as an example of a permanent magnet embedded rotor. However, the present invention is not limited to this and may be applied to a so-called magnetless rotor that does not include a permanent magnet. In this case, since the portion where the magnetic flux from the stator passes in the outer peripheral portion of the rotor and the vicinity thereof correspond to a region having a relatively large calorific value, the first hole portion is provided close to the region, and the above The second hole may be formed in a low heat generation region that is relatively far from the region. In this case, the first and second holes may constitute a flux barrier or may be formed separately from the flux barrier.

  DESCRIPTION OF SYMBOLS 10 Rotating electrical machine, 12 Rotor, 14 Stator, 15a Stator core, 15b Stator coil, 16 Case, 17 End wall, 17a Oil suction hole part, 18 Rotating shaft, 20 Shaft part, 21 Contact part, 22 Flange part, 22 Flange part , 23 Recess, 24 Bearing member, 26 Cooling medium passage, 27 Oil discharge hole, 28 Oil piping, 30 Pump, 32, 60 End plate, 33 Oil discharge hole, 36 Flow rate adjusting member, 38 Caulking member, 40 Rotor core, 42 Shaft Insertion hole, 44 refrigerant storage part, 45 bottom part, 46 magnetic pole, 48 permanent magnet, 50 first hole part, 52 second hole part, 54 bridge part, 56 first refrigerant path, 58 second refrigerant path, C oil surface, da, db, dc width, R1 radius.

Claims (9)

A rotor comprising a rotating shaft and a rotor core fixed to the outer periphery thereof,
The rotor core includes a first hole formed to extend in the axial direction in a region where the amount of heat generated during rotation is relatively large, and a second hole formed to extend in the axial direction in a region where the amount of heat generated is relatively small. A refrigerant reservoir that receives the cooling medium via the shaft portion of the rotating shaft, adjacent to the openings of the first hole portion and the second hole portion, outside the axial end portion of the rotor core. A first flow rate adjusting member disposed between the refrigerant reservoir and each opening of the first hole and the second hole, and the flow rate adjusting member communicates with the opening of the first hole; A rotor which forms a refrigerant passage and a second refrigerant passage communicating with the second hole portion, and has an opening area of the first refrigerant passage set larger than an opening area of the second refrigerant passage. The rotor according to claim 1, wherein
A rotor having a permanent magnet embedded in the rotor core, wherein the first hole is formed in contact with the permanent magnet. The rotor according to claim 2, wherein
The pair of permanent magnets constitutes one magnetic pole, the pair of permanent magnets are arranged apart from each other in the circumferential direction, and the first hole portion is in contact with the radially inner ends of the pair of permanent magnets. And the second hole is formed between the two first holes. The rotor according to claim 2 or 3,
The first and second holes constitute a flux barrier against magnetic flux from the permanent magnet. The rotor according to any one of claims 1 to 4,
The rotating shaft has a flange portion that protrudes radially outward from an outer peripheral surface thereof and has a concave portion formed on a surface facing the rotor core, and the refrigerant storage portion is formed by the concave portion and the flow rate adjusting member. A rotor formed by a partitioned space. The rotor according to any one of claims 1 to 4,
The rotor core further includes an end plate disposed on the outer side in the axial direction of the rotor core, and the end plate has a recess formed on a surface facing the rotor core, and the refrigerant storage portion includes the recess, the flow rate adjusting member, A rotor formed by a space partitioned by The rotor according to any one of claims 1 to 6,
The flow rate adjusting member is constituted by an annular plate disposed between the rotor core and the refrigerant reservoir, and the first and second refrigerant passages are formed from a notch formed in an inner peripheral portion of the flow rate adjusting member. And the width of the cut portion of the first refrigerant passage is set wider than the width of the second refrigerant passage. The rotor according to claim 7, wherein
The rotor core is a plate-like member laminate, and the annular plate is formed by a part of the plate-like member.   A rotary electric machine comprising the rotor according to any one of claims 1 to 8 and a stator disposed on an outer periphery of the rotor.

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