Rotor and rotating motor

Abstract

The present invention provides a rotor and a rotary electric machine that can drive efficiently by fully ensuring the flow rate of a refrigerant and controlling the flow rate of the refrigerant according to the rotation speed. The rotor (14) includes a rotor shaft (16) and a rotor body (17) fixedly engaged with the rotor shaft, the rotor shaft having a refrigerant flow path (16a) formed in the rotor shaft and through which cooling oil flows, and a refrigerant supply portion (16b) connecting the refrigerant flow path with the outer peripheral surface of the rotor shaft, the rotor body having a plate flow path (47) formed in the rotor body and connected to the refrigerant supply portion, and an iron core flow path (38) branched from the plate flow path in an axially extending manner, and a refrigerant adjustment portion (44) is provided in the plate flow path, and the refrigerant adjustment portion is adjusted in a manner that the flow rate of cooling oil supplied from the refrigerant supply portion to the iron core flow path is reduced as the rotation speed of the rotor body increases.

Description

Technical Field

[0001] The invention relates to a rotor and a rotating electric machine. Background Art

[0002] As a rotating electric machine such as a motor, there is known a rotating electric machine having a stator formed in a cylindrical shape and wound with a coil and a rotor rotatably arranged in the radial center of the stator. The rotor has a shaft, a rotor body fitted and fixed to the outer peripheral surface of the shaft, and a magnet provided on the rotor body. If power is supplied to the coil under the premise of such a structure, a cross-linked magnetic flux is formed in the stator. Magnetic attraction and repulsion are generated between the cross-linked magnetic flux and the magnet of the rotor, so that the rotor continues to rotate.

[0003] Here, the temperature rise of the magnet becomes the cause of demagnetization, which is closely related to the performance of the rotating electrical machine. Therefore, various technologies for effectively cooling the rotor have been proposed. For example, in Patent Document 1 (Japanese Patent Gazette No. 2019-161750), a refrigerant flow path for supplying refrigerant and a refrigerant supply portion for supplying refrigerant to the rotor body are provided on the shaft. An inner core flow path extending axially inside the rotor body is provided in the rotor body, and a refrigerant distribution plate is sandwiched therebetween. The refrigerant distribution plate has the function of connecting the refrigerant supply portion with the inner core flow path.

[0004] Under the premise of such a structure, the refrigerant is supplied in the order of the refrigerant flow path of the shaft, the refrigerant supply portion, and the refrigerant distribution plate, and the refrigerant is further supplied to the flow path in the core. Thus, the rotor can be cooled effectively. Summary of the invention

[0005] Problems to be solved by the present invention

[0006] However, in the above-described conventional technology, as the rotation speed of the rotor increases, the temperature of the rotating electrical machine increases, and thus the flow rate of the refrigerant increases.

[0007] However, if the flow rate of the refrigerant is increased, the friction generated by the refrigerant increases. In order to rotate the rotor at a desired rotation speed, a large amount of energy corresponding to the increase in friction is required, which has caused a problem that the rotating electrical machine cannot be driven efficiently.

[0008] Therefore, the present invention provides a rotor and a rotating electrical machine that can efficiently drive while sufficiently ensuring the flow rate of the refrigerant and controlling the flow rate of the refrigerant according to the rotation speed.

[0009] In order to solve the above-mentioned problems, a rotor and a rotating electric machine according to the present invention have the following structures.

[0010] (1) A rotor according to one embodiment of the present invention comprises: a rotor shaft that rotates around a rotation axis; and a rotor body that is fitted and fixed to the rotor shaft and rotates integrally with the rotor shaft, the rotor shaft having: a refrigerant flow path that is formed in the rotor shaft along the rotation axis and through which refrigerant flows; and a refrigerant supply portion that connects the refrigerant flow path with the outer peripheral surface of the rotor shaft, the rotor body having: a first flow path that is formed in the rotor body along a radial direction intersecting the rotation axis and connected to the refrigerant supply portion; and a second flow path that is branched from the first flow path in a manner extending along the rotation axis, a refrigerant adjustment portion being provided in the first flow path, the refrigerant adjustment portion adjusting the flow rate of the refrigerant supplied from the refrigerant supply portion to the second flow path in a manner that reduces as the rotation speed of the rotor body increases.

[0011] According to the scheme (1), the flow rate of the refrigerant supplied from the refrigerant supply unit to the second flow path can be adjusted in a manner that decreases as the rotation speed of the rotor body increases. The second flow path is farther away from the rotor shaft than the refrigerant flow path, the refrigerant supply unit, and the first flow path. By reducing the flow rate of the refrigerant supplied to the second flow path, the influence of the friction generated by the refrigerant on the rotor body can be reduced. Therefore, the flow rate of the refrigerant can be sufficiently ensured while the rotor can be driven efficiently.

[0012] (2) In the rotor of the above-mentioned scheme (1), the refrigerant adjustment portion may also include an elastic deformation portion, and the elastic deformation portion is adjusted in the following manner: it is elastically deformed under the action of the centrifugal force generated by the rotation of the rotor body to reduce the flow rate of the refrigerant supplied to the second flow path.

[0013] According to the aspect (2), the flow rate of the refrigerant can be adjusted using a simple elastic deformation portion by utilizing the centrifugal force generated by the rotation of the rotor body. Therefore, the rotor can be made smaller and less expensive.

[0014] (3) In the rotor according to the above-mentioned aspect (2), the elastic deformation portion may be a spring.

[0015] According to the aspect (3), the structure of the elastic deformation portion can be simplified.

[0016] (4) In the rotor of the above-mentioned scheme (3), the refrigerant adjustment unit may also include: a valve, which is arranged to be movable along the first flow path; a connecting path, which connects the second flow path with the first flow path, and opens and closes the first connecting port connected to the first flow path by moving the valve; and a recessed portion, which is arranged between the connecting path and the first flow path and is arranged at a position closer to the refrigerant supply unit than the valve, and the recessed portion is arranged in a manner that connects the connecting path with the first flow path and accommodates the valve, and the elastic deformation portion applies force to the valve toward the recessed portion.

[0017] According to the aspect (4), the valve can be displaced by the centrifugal force acting on the valve, thereby opening and closing the valve relative to the first communication port. In this way, the structure of the refrigerant adjustment unit can be simplified.

[0018] (5) In the rotor of the above-mentioned scheme (4), a cutout portion may be formed on the inner side surface in the direction of force applied by the elastic deformation portion in the recess, and the cutout portion connects the upstream side and the downstream side of the refrigerant in the recess when the valve is in contact with the inner side surface.

[0019] According to the aspect (5), even when the valve is in contact with the inner side surface of the recess, the flow of the refrigerant can be prevented from being cut off by the valve. Therefore, the refrigerant can be stably supplied to the communication passage and the second flow passage, especially at low rotation speeds of the rotor.

[0020] (6) In the rotor of the above-mentioned scheme (3), the refrigerant adjustment unit may also include: a sliding valve, which is configured to be movable along the first flow path and is formed with a through hole that can connect the first flow path with the second flow path; a first stopper, which limits the movement of the sliding valve toward the refrigerant supply unit at a position where the through hole is connected to the second flow path; and a second stopper, which limits the movement of the sliding valve to a side opposite to the refrigerant supply unit at a position where the connection between the through hole and the second flow path is cut off, and the elastic deformation unit applies a force to the sliding valve toward the first stopper.

[0021] According to the aspect (6), the slide valve can be displaced by the centrifugal force acting on the slide valve, thereby connecting or disconnecting the first flow path and the second flow path. In this way, the structure of the refrigerant adjustment unit can be simplified.

[0022] (7) In the rotor of the above-mentioned scheme (3), the elastic deformation portion may also be a leaf spring extending along the radial direction for opening and closing a second connecting port connected to the second flow path, and the elastic deformation portion includes: a counterweight, which is arranged at the radial outer end of the elastic deformation portion; and a fixing portion, which is arranged at the radial inner end of the elastic deformation portion and fixes the elastic deformation portion to the first flow path, and the elastic deformation portion is inclined in a manner of moving away from the second connecting port as it moves from the fixing portion toward the radial outer side when no centrifugal force generated by the rotation of the rotor body is applied.

[0023] According to the scheme (7), the second connecting port is not blocked when the rotor rotates at a low speed, and the centrifugal force acting on the counterweight deforms the leaf spring when the rotor rotates at a high speed, so that the leaf spring blocks the second connecting port. In this way, the structure of the refrigerant adjustment unit can be simplified by the leaf spring and the counterweight.

[0024] (8) In the rotor of the above-mentioned aspect (7), the elastic deformation portion may include a hole portion having a diameter smaller than an inner diameter of the second communication port.

[0025] According to the aspect (8), it is possible to prevent the second communication port from being completely blocked by the leaf spring, thereby making it possible to sufficiently maintain the cooling capacity of the rotor.

[0026] (9) A rotating electrical machine according to one aspect of the present invention includes: the above-mentioned rotor; and a stator formed so as to surround the outer circumference of the rotor and generating a magnetic field that applies a rotational force to the rotor.

[0027] According to the aspect (9), the rotor can be sufficiently cooled regardless of the rotation speed of the rotor, and the rotating electrical machine can be driven efficiently.

[0028] (10) In the rotating electric machine of the above-mentioned scheme (9), the rotating electric machine may also include at least one of a transmission for changing the speed of the rotation of the rotor and outputting it and a drive transmission unit for transmitting the rotation of the rotor to an axle, and the rotor shaft may include a transmission device refrigerant supply unit for supplying the refrigerant to at least one of the transmission and the drive transmission unit.

[0029] According to the aspect (10), the coolant can be supplied to the transmission and the drive transmission unit via the rotor shaft. The flow path of the coolant can be shared by the rotor, the transmission and the drive transmission unit, thereby reducing the number of components of the rotating electrical machine.

[0030] Effects of the Invention

[0031] According to the present invention, the flow rate of the refrigerant is sufficiently ensured and the flow rate of the refrigerant is controlled according to the rotation speed, so that the rotor and the rotating electric machine can be driven efficiently. BRIEF DESCRIPTION OF THE DRAWINGS

[0032] Figure 1 It is a cross-sectional view of the power unit 1 in the embodiment of the present invention.

[0033] Figure 2 This is a cross-sectional perspective view of a part of a rotor body and a rotor shaft in an embodiment of the present invention.

[0034] Figure 3 It is a perspective view of a first rotor core in the embodiment of the present invention.

[0035] Figure 4 It is an exploded perspective view of the oil passage plate in the first embodiment of the present invention.

[0036] Figure 5 This is an enlarged perspective view of the refrigerant adjustment unit in the first embodiment of the present invention.

[0037] Figure 6 It is along Figure 5 A cross-sectional view along line A-A shows the rotor stopped.

[0038] Figure 7 It is an explanatory diagram showing the flow of cooling oil in the oil passing plate when the rotor is stopped in the first embodiment of the present invention.

[0039] Figure 8 It is along Figure 5 A cross-sectional view along line A-A shows the rotor rotating.

[0040] Fig. 9 It is an explanatory diagram showing the flow of cooling oil in the oil passing plate when the rotor rotates in the first embodiment of the present invention.

[0041] Fig.10 It is a cross-sectional view along the axial direction of the refrigerant adjustment portion when the rotor is stopped in the second embodiment of the present invention.

[0042] Fig.11 It is a cross-sectional view along the axial direction of the refrigerant adjustment portion when the rotor rotates in the second embodiment of the present invention.

[0043] Fig.12 It is a cross-sectional view along the axial direction of the refrigerant adjustment section when the rotor is stopped in the third embodiment of the present invention.

[0044] Fig.13 It is a cross-sectional view along the axial direction of the refrigerant adjustment portion when the rotor rotates in the third embodiment of the present invention.

[0045] Explanation of symbols:

[0046] 1…power unit (rotating electric machine), 2…speed reduction mechanism (transmission), 4…differential device (drive transmission unit), 6…transmission refrigerant supply unit, 10…motor (rotating electric machine), 11…stator, 14, 214, 314…rotor, 16…rotor shaft, 16a…refrigerant flow path, 16b…refrigerant supply unit, 17, 217, 317…rotor body, 38…core inner flow path (second flow path), 44, 244, 344…refrigerant adjustment unit, 47, 247, 347…plate inner flow path (first flow path), 50…plate spring (elastic deformation unit, spring), 50a…radial inner end portion ( Radial inner end), 50b…Radial outer end (radial outer end), 50c…Hole portion, 51…Counterweight, 52, 252, 352…Communication port (second communication port), 53…Fixed member (fixed portion), 61, 361…Coil spring (elastic deformation portion, spring), 62…Valve housing recess (recess), 62b…Inner side surface, 63…Valve, 64, 364…Communication passage, 65…Valve communication port (first communication port), 66…Cut portion, 70…Sliding valve, 71…Limiting member (second limiting member), 72…Valve limiting member (first limiting member), 73…Through hole (hole portion), J1…Axis of rotation. DETAILED DESCRIPTION

[0047] Next, embodiments of the present invention will be described based on the drawings.

[0048] <Power unit>

[0049] Figure 1 1 is a cross-sectional view of a power unit 1 of a vehicle using a motor (rotating electric machine) 10 according to the present embodiment.

[0050] like Figure 1 As shown, the power unit 1 includes a motor housing 5a and one end ( Figure 1 The invention relates to a transmission case 5b connected to the left end of the transmission case 5a, a motor 10 for driving the vehicle provided in the motor case 5a, a speed reduction mechanism 2 provided in the transmission case 5b and reducing the rotation speed of the motor 10, and a differential device 4 for distributing the power of the motor 10 to the left and right axles (output shafts) 3a and 3b of the vehicle. It should be noted that in the following description, the direction parallel to the rotation axis J of the rotor shaft 16 constituting the motor 10 is simply referred to as the axial direction, the rotation direction of the rotor shaft 16 is simply referred to as the circumferential direction, and the radial direction of the rotor shaft 16 is simply referred to as the radial direction.

[0051] <Motor>

[0052] The motor 10 is provided in the axial center of the motor case 5a. The motor 10 includes an annular stator 11 fitted and fixed to the inner peripheral surface of the motor case 5a, and a rotor 14 rotatably supported radially inside the stator 11.

[0053] A rotor coil 12 of, for example, a three-phase structure is wound around the stator 11. The rotor coil 12 is connected to an external power source (not shown) via a terminal board. When power is supplied from the external power source to the rotor coil 12 via the terminal board, interlinked magnetic flux is formed in the stator 11. The interlinked magnetic flux exerts a magnetic rotational force on the rotor 14.

[0054] The rotor 14 mainly includes a rotor shaft 16 and a rotor body 17, and the rotor body 17 is fitted and fixed to a position of the rotor shaft 16 corresponding to the stator 11. The rotor body 17 will be described in detail later.

[0055] The rotor shaft 16 is formed in a hollow shape, and its axis line is consistent with the rotation axis J. That is, the rotor shaft 16 rotates around the rotation axis J. The rotor shaft 16 extends in the axial direction of the motor housing 5a as a whole. The inside of the rotor shaft 16 is configured as a refrigerant flow path 16a along the axial direction. Cooling oil (refrigerant) flows in the refrigerant flow path 16a. As the cooling oil, for example, lubricating oil used to drive the power unit 1 can be used. However, it is not limited to this, as long as it can be a substance that can be used as a refrigerant.

[0056] The rotor shaft 16 has a plurality of refrigerant supply portions 16b formed at locations corresponding to the rotor body 17. The refrigerant supply portions 16b are holes that allow the outer peripheral surface of the rotor shaft 16 to communicate with the refrigerant flow path 16a in the radial direction. The rotor shaft 16 has expanded diameter portions 16c and 16d that expand the inner diameter of the refrigerant flow path 16a between locations corresponding to the vicinity of both axial ends of the rotor body 17 and both axial ends.

[0057] The axle 3b passes through the refrigerant flow path 16a of the rotor shaft 16 with a small gap S1 between the axle 3b and the inner circumferential surface of the rotor shaft 16. Therefore, the axis of the axle 3b also coincides with the rotation axis J. The axle 3b protrudes from both axial ends of the rotor shaft 16. One end ( Figure 1 The left end in ( ) 3c extends to the differential device 4.

[0058] Both ends of the rotor shaft 16 in the axial direction are rotatably supported by the motor case 5 a via bearings 18 a , 18 b , and 18 c provided in the motor case 5 a .

[0059] A resolver rotor 20 a constituting a part of the resolver 20 is provided on the rotor shaft 16 on the opposite side to the speed reduction mechanism 2 across the rotor body 17 . The resolver 20 detects the rotational position of the rotor shaft 16 .

[0060] The resolver stator 20b constituting the other part of the resolver 20 is formed in an annular shape so as to surround the periphery of the resolver rotor 20a. The resolver stator 20b is fixed to the motor case 5a. The resolver coil 20c is wound around the resolver stator 20b.

[0061] The resolver 20 configured in this manner changes the current flowing through the resolver coil 20 c as the resolver rotor 20 a rotates, and the position of the rotor 14 can be detected by detecting the change in the current.

[0062] One end 16e of the rotor shaft 16 on the speed reduction mechanism 2 side protrudes toward the transmission case 5b via a bearing 18a. The speed reduction mechanism 2 is connected to the one end 16e.

[0063] <Reduction Mechanism>

[0064] The speed reduction mechanism 2 is composed of two-stage planetary gear mechanisms 21 a and 21 b (a first-stage planetary gear mechanism 21 a and a second-stage planetary gear mechanism 21 b ).

[0065] The first-stage planetary gear mechanism 21a includes: a first sun gear 22a fixed to the outer circumferential surface of one end 16e of the rotor shaft 16; a plurality of first planetary gears 23a meshing with the first sun gear 22a; a first planetary gear carrier 24a rotatably supporting the first planetary gears 23a; and a cylindrical first internal gear 25a meshing with each first planetary gear 23a. The outer circumferential surface of the first internal gear 25a is fitted and fixed to the inner circumferential surface of the transmission case 5b.

[0066] The second-stage planetary gear mechanism 21b includes: a second sun gear 22b protruding from the first planetary gear carrier 24a toward the side opposite to the motor 10 and rotating integrally with the first planetary gear carrier 24a; a plurality of second planetary gears 23b meshing with the second sun gear 22b; a second planetary gear carrier 24b supporting the second planetary gears 23b so as to rotate freely; and a cylindrical second internal gear 25b meshing with each second planetary gear 23b. A small gap S2 is formed between the second sun gear 22b and the axle 3b. The outer peripheral surface of the second internal gear 25b is fitted and fixed to the inner peripheral surface of the transmission case 5b.

[0067] Under such a configuration, when the first sun gear 22a rotates integrally with the rotor shaft 16, the first planetary gears 23a meshing with the first sun gear 22a rotate around the outer circumference of the first sun gear 22a while rotating.

[0068] The second sun gear 22b rotates integrally with the first planetary gear carrier 24a. When the second sun gear 22b rotates, the second planetary gears 23b meshing with the second sun gear 22b revolve around the outer circumference of the second sun gear 22b while rotating. As a result, the second planetary gear carrier 24b rotates around the rotation axis C.

[0069] In this way, the rotation of the rotor shaft 16 is reduced in speed and transmitted to the second planetary carrier 24b. The differential device 4 is connected to the second planetary carrier 24b.

[0070] <Differential gear>

[0071] The differential device 4 includes a differential case 26 that transmits the rotation of the second carrier 24 b , a pinion gear 27 that is rotatably supported in a protruding manner in the differential case 26 , and a pair of side gears 28 a and 28 b that mesh with the pinion gear 27 .

[0072] The pinion gear 27 is supported to be rotatable about a direction perpendicular to the rotation axis J, and rotates integrally with the differential case 26 around the rotation axis J. The side gears 28a and 28b are arranged on both sides with the pinion gear 27 sandwiched therebetween. The side gears 28a and 28b are provided coaxially with the axles 3a and 3b at one end 3c of each axle 3a and 3b. The side gears 28a and 28b rotate integrally with the corresponding axles 3a and 3b.

[0073] <Rotor body>

[0074] Figure 2 It is a cross-sectional perspective view of a part of the rotor body 17 and the rotor shaft 16 .

[0075] like Figure 2 As shown in FIG. 1 , the rotor body 17 includes two cylindrical rotor cores 30a and 30b (a first rotor core 30a and a second rotor core 30b) fitted and fixed to the outer peripheral surface of the rotor shaft 16, a disc-shaped oil pass plate 31 provided between the two rotor cores 30a and 30b, and a plurality of magnets 32 provided on the outer peripheral surface of each rotor core 30a and 30b. That is, the rotor 14 is a so-called SPM (Surface Permanent Magnet) type rotor.

[0076] The rotor body 17 is provided with an oil passage plate 31 at a position where the refrigerant supply portion 16b is formed on the rotor shaft 16. The rotor body 17 rotates integrally with the rotor shaft 16.

[0077] Since the two rotor cores 30a and 30b have the same structure, in the following description, only the first rotor core 30a of the two rotor cores 30a and 30b will be described, and the second rotor core 30b will be denoted by the same reference numerals and description thereof will be omitted. The second rotor core 30b will be described as necessary.

[0078] Figure 3 It is a perspective view of the first rotor core 30a.

[0079] like Figure 2 , Figure 3 As shown, the axis of the first rotor core 30a coincides with the rotation axis J. The first rotor core 30a can be formed by laminating a plurality of electromagnetic steel sheets or by pressurizing soft magnetic powder. A through hole 33 is formed in the radial center of the first rotor core 30a and penetrates in the axial direction. The rotor shaft 16 is pressed or inserted into the through hole 33. When the rotor shaft 16 is inserted, the first rotor core 30a is fixed to the rotor shaft 16 by, for example, an adhesive or the like.

[0080] On the outer peripheral surface of the first rotor core 30a, a plurality of (e.g., 8 in the present embodiment) magnet housing recesses 34 for arranging the magnets 32 are formed at equal intervals in the circumferential direction. The magnet housing recesses 34 are formed over the entire axial direction of the first rotor core 30a. By forming the magnet housing recesses 34, a salient pole 35 having a convex strip is formed between adjacent magnet housing recesses 34 in the circumferential direction, and the salient pole 35 is formed over the entire axial direction. The salient pole 35 can be used to obtain a reluctance torque based on the interlinked magnetic flux formed in the stator 11.

[0081] The salient pole 35 has a cutout portion 36 formed by cutting off the corner of the salient pole 35 at the radially outer end and on both circumferential sides. The cutout portion 36 forms a step portion 36a between the radially outer side surface of the salient pole 35 and the magnet housing recess 34.

[0082] On the first rotor core 30a, a first flux barrier 37 penetrating in the axial direction is formed on the radial inner side of each salient pole 35. The first flux barrier 37 is used to block the flow of magnetic flux. The first flux barrier 37 functions as an inner core flow path 38 for cooling oil (refrigerant) to flow. That is, the inner core flow path 38 extends in the axial direction.

[0083] A plurality of second magnetic flux barriers 39 are formed in the first rotor core 30a at a position radially inward of the first magnetic flux barrier 37 so as to surround the through hole 33. Each second magnetic flux barrier 39 is formed to penetrate the entire first rotor core 30a in the axial direction. Each second magnetic flux barrier 39 is arranged at equal intervals in the circumferential direction. The second magnetic flux barriers 39 are also used to block the flow of magnetic flux.

[0084] In the magnet receiving recess 34 of the first rotor core 30a, magnets 32 are respectively arranged. The magnets 32 are bent along the outer peripheral surface of the first rotor core 30a when viewed from the axial direction. As the magnets 32, various magnets such as ferrite sintered magnets, ferrite bonded magnets, neodymium bonded magnets, and neodymium sintered magnets can be used. In a state where the magnets 32 are arranged in the magnet receiving recess 34, a gap corresponding to the amount of the cutout portion 36 is formed between the radially outer peripheral portion of the salient pole 35 in the circumferential direction and the magnets 32.

[0085] Since the first magnetic flux barrier 37 is formed on the first rotor core 30a, it is possible to suppress the magnetic flux of the magnet 32 ​​from circling around the magnets 32 adjacent to each other in the circumferential direction and leaking. Since the plurality of second magnetic flux barriers 39 are formed on the first rotor core 30a, it is also possible to suppress the magnetic flux of the magnet 32 ​​from leaking to the rotor shaft 16 via the first rotor core 30a.

[0086] A cylindrical magnet cover 40 is provided on the outer peripheral surfaces of the first rotor core 30a, the second rotor core 30b, and the oil passing plate 31 to cover the magnet 32 ​​from above. Figure 2 , Figure 3 In order to make it easier to understand the shapes of the first rotor core 30a and the second rotor core 30b, the magnet cover 40 is shown in a transparent state (using a two-dot chain line).

[0087] The magnet cover 40 is formed, for example, by fiber winding. Fiber winding is a method of forming by winding a plurality of carbon fiber bundles impregnated with resin around a mandrel. A hole 41 extending in the axial direction is formed by such a magnet cover 40, the cutout portion 36 (step portion 36a), and the circumferential side surface of the magnet 32. The hole 41 also functions as a small flow path 42 for cooling oil (refrigerant) to flow.

[0088] [First embodiment]

[0089] <Oil passing plate>

[0090] Figure 4 It is an exploded perspective view of the oil passage plate 31 in the first embodiment.

[0091] like Figure 2 , Figure 4 As shown in FIG. 1 , the oil passing plate 31 includes two circular plates 43a and 43b (a first plate 43a and a second plate 43b) overlapped in the axial direction and a refrigerant adjustment portion 44 provided between the two plates 43a and 43b. Since the two plates 43a and 43b have the same structure, in the following description, only the first plate 43a of the two plates 43a and 43b will be described, and the second plate 43b will be marked with the same reference numeral and the description will be omitted. The second plate 43b will be described as needed.

[0092] The outer diameter of the first plate 43a is substantially the same as the outer diameter of each rotor core 30a, 30b. A plate recess 43d is formed on most of the facing surface 43c of the first plate 43a on the second plate 43b side. The openings 47a of each plate 43a, 43b thus formed overlap each other, so that the plate recess 43d of each plate 43a, 43b constitutes a plate inner flow path 47 isolated from the outside. That is, the plate inner flow path 47 extends in the radial direction.

[0093] The radial center of the first plate 43a coincides with the rotation axis J. A through hole 45 is formed in the radial center of the first plate 43a so as to penetrate the first plate 43a in the thickness direction. The rotor shaft 16 is pressed or inserted into the through hole 45. When the rotor shaft 16 is inserted, the first plate 43a is fixed to the rotor shaft 16 by, for example, an adhesive or the like.

[0094] Since the oil passing plate 31 is disposed at a position on the rotor shaft 16 where the refrigerant supply portion 16 b is formed, the plate intra-plate flow path 47 of the oil passing plate 31 communicates with the refrigerant supply portion 16 b .

[0095] The first plate 43a has a plurality of (eg, four in the first embodiment) spring housing recesses 46 formed at equal intervals in the circumferential direction around the through hole 45. Parts of the leaf springs 50 constituting the refrigerant adjustment unit 44 are housed in each of the spring housing recesses 46.

[0096] The spring receiving recess 46 is a portion for receiving a leaf spring 50, which will be described later, constituting the refrigerant adjusting portion 44. The spring receiving recess 46 is a rectangular shape that is long in the radial direction when viewed from the axial direction, and is formed between the peripheral edge of the through hole 45 and a portion slightly outside the radial center of the first plate 43a. The radial inner end of the spring receiving recess 46 is connected to the through hole 45. In other words, the bottom 46a of the spring receiving recess 46 is connected to the through hole 45. The bottom 46a of the spring receiving recess 46 is formed slightly inclined so that the depth of the spring receiving recess 46 gradually becomes shallower as it moves from the through hole 45 toward the radial outer side.

[0097] The refrigerant adjustment part 44 includes a counterweight 51 provided on the leaf spring 50 and a communication port 52 formed on the first plate 43a in addition to the leaf spring 50. A plurality of refrigerant adjustment parts 44 are provided at equal intervals in the circumferential direction (for example, four in the first embodiment) in a manner corresponding to the spring storage recess 46 of the first plate 43a. Figure 4 In the figure, the leaf spring 50 and the weight 51 provided on the second plate 43b side are omitted.

[0098] The leaf spring 50 is formed in a strip shape extending radially from the periphery of the through hole 45 of the first plate 43a to the front of the inner peripheral surface 43e of the plate recess 43d. The radial inner half of the leaf spring 50 is accommodated in the spring accommodation recess 46. The radial inner end 50a of the leaf spring 50 is fixed to the bottom 46a of the spring accommodation recess 46 via a fixing member 53 such as a rivet.

[0099] The leaf spring 50 is elastically deformed in a direction approaching or moving away from the bottom 43f of the plate recess 43d. Since the bottom 46a of the spring receiving recess 46 is formed obliquely, the leaf spring 50 fixed to the bottom 46a gradually moves away from the bottom 43f of the plate recess 43d as it moves radially outward in a no-load state.

[0100] Note that, instead of forming the bottom portion 46a to be inclined, the leaf spring 50 may be slightly bent so that the leaf spring 50 gradually separates from the bottom portion 43f of the plate recess 43d as it moves radially outward in a no-load state.

[0101] A hole portion 50 c is formed substantially at the center of the leaf spring 50 in the longitudinal direction.

[0102] The weight 51 is provided at the radially outer end 50b of the leaf spring 50. Even with the weight 51, the leaf spring 50 maintains a posture where it gradually moves away from the bottom 43f of the plate recess 43d as it moves radially outward in a state where no external force acts (no load state).

[0103] A retreat groove 54 for avoiding contact with the counterweight 51 is formed on the first plate 43a at a position corresponding to the counterweight 51. A communication port 52 is formed between the retreat groove 54 and the spring housing recess 46 and at a position overlapping with the hole 50c of the leaf spring 50 so as to penetrate the first plate 43a in the thickness direction.

[0104] A wide mouth portion 55 having an opening area larger than that of the communication port 52 is formed at a position corresponding to the communication port 52 on the back surface 43g of the first plate 43a on the opposite side to the facing surface 43c. The wide mouth portion 55 constitutes a part of the communication port 52. The wide mouth portion 55 (communication port 52) ​​communicates with a part of the plurality of core-internal flow paths 38 formed in each of the rotor cores 30a and 30b. In this way, the flow path branches from the plate-internal flow path 47 extending in the radial direction to the core-internal flow path 38 extending in the axial direction via the wide mouth portion 55 (communication port 52).

[0105] The diameter of the communication port 52 is such that the communication port 52 is blocked by the leaf spring 50 when the leaf spring 50 contacts the bottom 43f of the plate recess 43d due to elastic deformation of the leaf spring 50. That is, the leaf spring 50 opens and closes the communication port 52. The diameter of the hole 50c of the leaf spring 50 is smaller than the diameter of the communication port 52.

[0106] <Function of the rotor and flow of cooling oil>

[0107] Next, based on Figure 1 and Figures 5 to 9 The function of the rotor 14 and the flow of the cooling oil will be described.

[0108] like Figure 1 As shown, cooling oil is supplied to the refrigerant flow path 16a of the rotor shaft 16 from the other end 16f of the rotor shaft 16 on the opposite side to the speed reduction mechanism 2 (see Figure 1 The cooling oil flows through the small gap S1 between the refrigerant flow path 16a and the axle 3b and spreads throughout the entire axial direction of the rotor shaft 16 (see arrow Y1 in FIG. 1 ). Figure 1 arrow Y2 in the figure).

[0109] Then, cooling oil is supplied to the speed reduction mechanism 2 side via the one end 16e of the rotor shaft 16 (see Figure 1 The cooling oil is supplied to the differential device 4 through the small gap S2 between the second sun gear 22b and the axle 3b (see arrow Y3 in FIG. Figure 1 Arrow Y4 in the figure).

[0110] By forming the rotor shaft 16 into a hollow shape as described above, the opening 16 g at the one end 16 e of the rotor shaft 16 functions as the transmission refrigerant supply portion 6 for supplying cooling oil to the transmission such as the speed reduction mechanism 2 .

[0111] Cooling oil also flows in the small flow path 42 formed in the rotor body 17. The cooling oil flowing in the refrigerant flow path 16a is supplied to the plate in-plate flow path 47 of the oil passing plate 31 via the refrigerant supply portion 16b of the rotor shaft 16 (see Figure 1 arrow Y5).

[0112] Hereinafter, the operation of the oil passing plate 31 will be described separately for the case when the rotor 14 is stopped and the case when the rotor 14 is rotating.

[0113] First, based on Figure 5 to Figure 7 The case where the rotor 14 stops will be described.

[0114] Figure 5 It is an enlarged perspective view of the refrigerant adjustment portion 44 in the oil passage plate 31 . Figure 6 It is along Figure 5 The cross-sectional view along the line AA shows the rotor 14 when it is stopped. Figure 7 3 is an explanatory diagram showing the flow of cooling oil in the oil passing plate 31 when the rotor 14 is stopped. Figure 7 The symbols Y1, Y5 and Figure 1 The symbols Y1 and Y5 correspond to (the following Fig. 9 Same).

[0115] First, when the rotor 14 stops, no external force acts on the refrigerant adjustment portion 44. That is, the leaf spring 50 gradually moves away from the bottom 43f of the plate recess 43d as it moves radially outward. Figure 6 As shown in detail in FIG. 1 , the communication ports 52 of the plates 43 a and 43 b are not blocked by the leaf springs 50 , and the communication ports 52 are open.

[0116] As a result, if Figure 5 to Figure 7 As shown, the cooling oil supplied to the plate inner flow path 47 flows from the gap K between the bottom 43f of the plate recess 43d and the plate spring 50 to the communication port 52 (see Figure 5 to Figure 7 arrow Y6).

[0117] The cooling oil is supplied to the core flow path 38 of each rotor core 30a, 30b through the communication port 52 (wide opening 55). Since the communication port 52 has the wide opening 55 on the back surface 43g side of each plate 43a, 43b, the cooling oil is smoothly supplied from the oil passing plate 31 to the core flow path 38. In this way, the cooling oil is fully distributed in each rotor core 30a, 30b without any omission, so that the entire rotor 14 is cooled.

[0118] Next, based on Figure 8 , Fig. 9 The following describes the situation when the rotor 14 rotates.

[0119] Figure 8 is along with Figure 5 The figure corresponds to a cross-sectional view taken along line AA of FIG. 1 , and shows the rotor 14 rotating. Fig. 9 1 is an explanatory diagram showing the flow of cooling oil in the oil passing plate 31 when the rotor 14 rotates.

[0120] like Figure 8 , Fig. 9 As shown in FIG. 1 , when the rotor 14 rotates, a centrifugal force acts on the counterweight 51 of the refrigerant adjustment section 44, pulling the leaf spring 50 radially outward. Then, the leaf spring 50 is elastically connected to the bottom 43f of the plate recess 43d. As a result, the communication ports 52 of the plates 43a and 43b are blocked by the leaf spring 50 (see FIG. 1 ). Figure 8 Arrow Y7 in the figure).

[0121] Here, a hole portion 50c is formed at a position overlapping with the communication port 52 on the leaf spring 50. Therefore, even when the leaf spring 50 is in contact with the bottom 43f of the plate recess 43d, the communication port 52 is not completely blocked by the leaf spring 50, and the cooling oil flows to the communication port 52 through the hole portion 50c. However, the diameter of the hole portion 50c is smaller than the diameter of the communication port 52. Therefore, compared with the case where the communication port 52 is open (the case where the rotor 14 is stopped), the flow rate of the cooling oil supplied to the iron core internal flow path 38 of each rotor iron core 30a, 30b is reduced.

[0122] The pulling force acting on the leaf spring 50 in the radial direction outward also changes under the centrifugal force acting on the counterweight 51. That is, when the rotation speed of the rotor 14 increases, the centrifugal force acting on the counterweight 51 increases accordingly. As a result, the pulling force acting on the leaf spring 50 in the radial direction outward also increases, and accordingly the floor spring 50 is elastically deformed to a large extent toward the bottom 43f of the plate recess 43d, so that the leaf spring 50 is reliably in contact with the bottom 43f of the plate recess 43d.

[0123] On the other hand, when the rotation speed of the rotor 14 is low, the centrifugal force acting on the counterweight 51 is also reduced accordingly. As a result, although the leaf spring 50 is close to the bottom 43f of the plate recess 43d, a small gap is generated between the bottom 43f and the leaf spring 50. However, compared with when the rotor 14 is stopped, the gap K between the bottom 43f and the leaf spring 50 is smaller, so the flow rate of the cooling oil supplied to the communication port 52 is reduced accordingly.

[0124] Thus, the rotor 14 includes: a rotor shaft 16 having a refrigerant flow path 16a and a refrigerant supply portion 16b; and a rotor body 17 fitted and fixed to the outer peripheral surface of the rotor shaft 16. The rotor body 17 includes two rotor cores 30a and 30b and an oil passing plate 31 provided between the two rotor cores 30a and 30b. The refrigerant adjustment portion 44 provided on the oil passing plate 31 allows sufficient cooling oil to be supplied from the refrigerant supply portion 16b to the core inner flow path 38 of each rotor core 30a and 30b when the rotor 14 stops. In contrast, when the rotor 14 rotates, the supply of refrigerant from the refrigerant supply portion 16b to the core inner flow path 38 of each rotor core 30a and 30b is reduced.

[0125] In this way, the refrigerant adjustment unit 44 can adjust the flow rate of the refrigerant supplied from the refrigerant supply unit 16b to the core inner flow path 38 in a manner that decreases as the rotation speed of the rotor 14 (rotor body 17) increases. The core inner flow path 38 is located radially outward of the refrigerant flow path 16a, the refrigerant supply unit 16b, and most of the plate inner flow path 47. Therefore, by reducing the flow rate of the cooling oil to the core inner flow path 38 when the rotor 14 rotates, the influence of the friction caused by the cooling oil on the rotor body 17 can be reduced. As a result, the rotor 14 can be driven efficiently while ensuring a sufficient flow rate of the cooling oil.

[0126] As the refrigerant adjustment part 44, a leaf spring 50 that is elastically deformed by the centrifugal force generated by the rotation of the rotor 14 is used. In addition, a counterweight 51 is used to sufficiently act the centrifugal force on the leaf spring 50. In this way, the flow rate of the cooling oil to the core flow path 38 can be adjusted with a simple structure. Therefore, the rotor 14 can be miniaturized and the cost can be reduced.

[0127] A hole 50c is formed at a position overlapping the communication port 52 on the leaf spring 50. The diameter of the hole 50c is smaller than the diameter of the communication port 52. Therefore, the communication port 52 is not completely blocked by the leaf spring 50, and cooling oil can be supplied to the core flow path 38 even when the rotation speed of the rotor 14 is high. As a result, the cooling capacity of the rotor 14 can be sufficiently maintained.

[0128] The rotor shaft 16 has a transmission refrigerant supply portion 6 provided on one end 16e side. Therefore, cooling oil can also be supplied to the speed reduction mechanism 2 and the differential device 4 via the rotor shaft 16. The flow path of cooling oil can be shared by the rotor 14, the speed reduction mechanism 2, and the differential device 4, so that the number of components of the power unit 1 can be reduced.

[0129] Furthermore, small flow paths 42 are formed near the outer peripheral surface of the rotor body 17 and on both circumferential sides of each magnet 32, and cooling oil also flows in these small flow paths 42. Therefore, cooling of the magnet 32 ​​can be promoted, and demagnetization caused by high temperature of the magnet 32 ​​can be suppressed.

[0130] It should be noted that in the first embodiment described above, the hole 50 c is formed in the leaf spring 50 . However, the present invention is not limited thereto, and the hole 50 c may not be formed. In this case, when the rotor 14 rotates, the communication port 52 is completely blocked by the leaf spring 50 .

[0131] [Second embodiment]

[0132] Next, use Figure 1 Based on Fig.10 , Fig.11 A second embodiment will be described.

[0133] Fig.10 It is a cross-sectional view along the axial direction of the refrigerant adjustment unit 244 in the second embodiment. Fig.10 Compared with the first embodiment described above Figure 7 It should be noted that the same reference numerals are given to the same structures as those in the first embodiment, and description thereof will be omitted (the same applies to the third embodiment described below).

[0134] like Figure 1 , Fig.10 As shown, in the second embodiment, the power unit 1 includes a motor 10, a speed reduction mechanism 2, and a differential device 4 arranged in a motor housing 5a and a transmission housing 5b, which is the same as the first embodiment described above. The motor 10 includes a stator 11 and a rotor 214, and the rotor 214 includes a hollow rotor shaft 16 and a rotor body 217, which is the same as the first embodiment described above. The rotor body 217 includes two rotor cores 30a, 30b and a disc-shaped oil passing plate 231 arranged between the two rotor cores 30a, 30b, which is the same as the first embodiment described above. It should be noted that the above point is also the same in the third embodiment described later.

[0135] <Refrigerant adjustment department>

[0136] Here, the difference between the first embodiment described above and the second embodiment is that the structure of the refrigerant adjustment unit 44 of the first embodiment is different from the structure of the refrigerant adjustment unit 244 of the second embodiment (the same applies to the third embodiment described below).

[0137] That is, the refrigerant adjustment part 244 includes: a connecting recess 60 formed in each plate 243a, 243b; a coil spring 61 disposed in the connecting recess 60; a valve receiving recess 62 connected to the connecting recess 60; and a spherical valve 63 received in the valve receiving recess 62. A plurality of refrigerant adjustment parts 244 (for example, four in the second embodiment) are provided at equal intervals in the circumferential direction.

[0138] The connecting recess 60 is formed between the position which is spaced radially outward from the through hole 245 (refrigerant supply portion 16b) formed in the radial center of each plate 243a, 243b to the front of the outer periphery of each plate 243a, 243b. The connecting recess 60 is formed along the radial direction in a manner that crosses the connecting opening 252 of each plate 243a, 243b. The depth H1 of the connecting recess 60 is slightly deeper than the depth H2 of the plate recess 243d.

[0139] A valve housing recess 62 is formed radially inside the communication recess 60. The radial inner end of the valve housing recess 62 is away from the through hole 245 of each plate 243a, 243b. That is, in the radial direction, the communication recess 60 and the plate recess 243d are connected via the valve housing recess 62. The bottom surface of the valve housing recess 62 is formed in an arc shape in a manner corresponding to the valve 63.

[0140] The depth H3 of the valve housing recess 62 is deeper than the depth H1 of the connecting recess 60 and the depth H2 of the plate recess 243d, and the radius of curvature is substantially the same as or slightly larger than the radius of the valve 63. The radial length of the valve housing recess 62 is a length that allows the valve 63 to move (roll) in the radial direction. On the connecting recess 60 side of the valve housing recess 62, an inclined surface 62a is formed so that the depth gradually becomes shallower as it approaches the connecting recess 60.

[0141] Under the premise of such a structure, the opposing surfaces 243c of each plate 243a, 243b are overlapped with each other, thereby forming a radially extending communication passage 64 that connects the plate internal flow passage 247 with the communication port 252 through two communication recesses 60. A valve communication port 65 that connects the communication passage 64 with the valve housing recess 62 is formed on the valve housing recess 62 side of the communication passage 64. The coil spring 61 is accommodated in the communication passage 64 in a state of compression deformation in the radial direction.

[0142] The valve 63 accommodated in the valve accommodation recess 62 is urged radially inward by the coil spring 61. When the valve 63 moves toward the communication path 64 side against the elastic force of the coil spring 61, the valve communication port 65 is closed by the valve 63.

[0143] Here, in the valve housing recess 62, a cutout portion 66 is formed on the inner side surface 62b (radially inner side surface 62b) in the urging direction of the coil spring 61. The cutout portion 66 prevents the opening 247a on the valve housing recess 62 side of the plate flow path 247 from being completely blocked even when the valve 63 is in contact with the inner side surface 62b. In other words, the cutout portion 66 connects the upstream side and the downstream side of the cooling oil when the valve 63 is in contact with the inner side surface 62b.

[0144] <Function of oil passing plate>

[0145] Next, the function of the oil passing plate 231 will be described.

[0146] First, based on Fig.10 The function of the oil passing plate 231 when the rotor 214 stops will be described.

[0147] like Fig.10As shown, when the rotor 214 stops, no external force acts on the refrigerant adjustment portion 244. That is, the valve 63 is urged toward the opening 247a of the plate inlet flow path 247 by the elastic force of the coil spring 61. At this time, the valve communication port 65 is open.

[0148] In this state, the plate is supplied to the flow path 247 (see Fig.10 The cooling oil (arrow Y8 in FIG. 1 ) is supplied to the core flow path 38 of each rotor core 30a, 30b via the cutout portion 66 of the valve housing recess 62, the valve housing recess 62, the valve communication port 65 and the communication path 64 (see FIG. 1 ). Fig.10 Arrow Y9 in the figure).

[0149] Next, based on Fig.11 The effect of the oil passing plate 231 when the rotor 214 rotates will be described.

[0150] Fig.11 It is a cross-sectional view along the axial direction of the refrigerant adjustment unit 244 when the rotor 214 rotates.

[0151] like Fig.11 As shown, when the rotor 214 rotates, centrifugal force acts on the valve 63, and the valve 63 moves radially outward in the valve housing recess 62 against the elastic force of the coil spring 61. Since the radial direction also follows the plate inner flow path 247, it can be said that the valve 63 moves along the plate inner flow path 247.

[0152] The valve 63 moves, thereby closing the valve communication port 65. Here, an inclined surface 62a is formed in the valve housing recess 62. Therefore, the valve 63 abuts against the inclined surface 62a, thereby reliably closing the valve communication port 65 by the valve 63. Thus, the supply of cooling oil to the core internal flow path 38 of each rotor core 30a, 30b can be cut off.

[0153] Therefore, according to the above-mentioned second embodiment, it is possible to achieve the same effects as those of the above-mentioned first embodiment.

[0154] It should be noted that, in the second embodiment described above, the bottom surface of the valve housing recess 62 is formed in an arc shape in a manner corresponding to the valve 63. However, it is not limited to this, and any shape can be used as long as it can limit the moving direction of the valve 63 in the radial direction. For example, the valve housing recess 62 can be formed in a V-groove shape or a square groove shape.

[0155] In the second embodiment described above, the following situation is described: when the valve 63 moves radially outward in the valve receiving recess 62 against the elastic force of the coil spring 61, the valve 63 blocks the valve communication port 65. However, the valve 63 may not completely block the valve communication port 65. For example, a portion such as the cutout portion 66 of the valve receiving recess 62 may be formed in the valve communication port 65. With such a configuration, the flow rate of the cooling oil supplied to the flow path 38 in the core may also be reduced.

[0156] [Third Embodiment]

[0157] <Refrigerant adjustment department>

[0158] Next, based on Fig.12 , Fig.13 A third embodiment will be described.

[0159] Fig.12 It is a cross-sectional view along the axial direction of the refrigerant adjustment unit 344 in the third embodiment. Fig.12 Compared with the first embodiment described above Figure 7 It should be noted that the same reference numerals are given to the same structures as those in the first embodiment, and the description thereof will be omitted.

[0160] like Fig.12 As shown, the refrigerant adjustment part 344 provided on the oil passing plate 331 of the rotor body 317 constituting the rotor 314 in the third embodiment includes a connecting recess 360 formed in each plate 343a, 343b and a slide valve 70, a stopper 71 and a coil spring 361 accommodated in the connecting recess 360. A plurality of refrigerant adjustment parts 344 (for example, four in the third embodiment) are provided at equal intervals in the circumferential direction.

[0161] The connecting recess 360 is formed between the following position and the outer periphery of each plate 343a, 343b, wherein the above-mentioned position is a position spaced apart from the through hole 345 (refrigerant supply part 16b) formed in the radial center of each plate 343a, 343b to the radial outside. The connecting recess 360 is formed in the radial direction in a manner of crossing the connecting opening 352 of each plate 343a, 343b. The cross section of the connecting recess 360 along the circumferential direction is formed in a polygonal shape. The depth H4 of the connecting recess 360 is deeper than the depth H5 of the plate recess 343d.

[0162] Under the premise of such a structure, the opposing surfaces of the plates 343a and 343b (at Fig.12The two connecting recesses 360 overlap each other, thereby forming a connecting passage 364 extending in the radial direction that connects the plate flow passage 347 with the connecting port 352. The slide valve 70 is provided so as to be movable along the connecting passage 364, that is, in the radial direction. A limited motion member 71 is provided on the opposite side of the connecting passage 364 to the plate flow passage 347 across the slide valve 70.

[0163] The slide valve 70 is formed into a polygonal columnar shape with the radial direction as the axial direction in a manner corresponding to the size of the communication passage 364 and the shape of the communication recess 360. The axis J2 of the slide valve 70 coincides with the radial direction. By making the shapes of the peripheral surfaces of the communication passage 364 and the slide valve 70 into polygonal shapes, the rotation of the slide valve 70 around the axis J2 relative to the communication passage 364 can be restricted. The inner side surface 360a on the through hole 345 side of the communication recess 360 constituting the communication passage 364 functions as a valve stopper 72 that restricts the movement of the slide valve 70 to the radial inner side (refrigerant supply portion 16b).

[0164] The slide valve 70 is provided with a through hole 73 along the axis J2. The through hole 73 is composed of three through holes 73a to 73c arranged along the axis J2 in the order of a first through hole 73a, a second through hole 73b having a smaller diameter than the first through hole 73a, and a third through hole 73c having a larger diameter than the first through hole 73a and the second through hole 73b from the radial inner side. The through holes 73a to 73c are connected to each other. The third through hole 73c disposed on the side of the stopper 71 functions as a spring receiving recess 74 for receiving the coil spring 361.

[0165] The slide valve 70 has two side communication holes 75 that communicate the outer side surface 70a of the slide valve 70 with the third through hole 73c. ​​The two side communication holes 75 are disposed at positions that can communicate with the communication ports 352 of the plates 343a and 343b, respectively.

[0166] The stopper 71 is formed to correspond to the size of the communication passage 364 and to correspond to the shape of the communication recess 360. The stopper 71 closes the radially outer opening 364a in the communication passage 364. The stopper 71 is fixed to the communication passage 364. The movement of the slide valve 70 to the radially outer side (the side opposite to the refrigerant supply portion 16b) is restricted by the stopper 71.

[0167] A spring receiving recess 76 is formed on the side surface 71a of the stopper 71 on the slide valve 70 side. The coil spring 361 is received in a compressed state between the spring receiving recess 76 and the spring receiving recess 74 of the slide valve 70. That is, the slide valve 70 is urged radially inward (toward the refrigerant supply portion 16b) by the coil spring 361.

[0168] Here, the stopper 71 is arranged so that when the radially outer end 70b of the slide valve 70 abuts against the stopper 71, the position of the side communication hole 75 of the slide valve 70 and the position of the communication port 352 of each plate 343a, 343b are offset in the radial direction. In this offset state, the side communication hole 75 and the communication port 352 do not partially overlap when viewed from the axial direction. On the other hand, the valve stopper 72 (inner surface 360a) is formed so that when the radially inner end 70c of the slide valve 70 abuts against the valve stopper 72, the position of the side communication hole 75 of the slide valve 70 and the position of the communication port 352 of each plate 343a, 343b are offset in the axial direction ( Fig.13 overlap in the up and down directions).

[0169] <Function of oil passing plate>

[0170] First, based on Fig.12 The function of the oil passing plate 331 when the rotor 314 stops will be described.

[0171] like Fig.12 As shown in FIG. 1 , when the rotor 314 stops, no external force acts on the refrigerant adjustment portion 344. That is, the slide valve 70 is urged toward the valve stopper 72 (the inner side surface 360a of the communication recess 360) by the elastic force of the coil spring 361. Therefore, the radial inner end 70c of the slide valve 70 abuts against the valve stopper 72, and the movement of the slide valve 70 toward the radial inner side (toward the refrigerant supply portion 16b) is restricted.

[0172] In this state, the position of the side communication hole 75 of the slide valve 70 overlaps with the position of the communication port 352 of each plate 343a, 343b in the axial direction. As a result, the refrigerant supply portion 16b is connected to the core internal flow path 38 of each rotor core 30a, 30b via the through hole 73 and the side communication hole 75 of the slide valve 70, the communication port 352 of each plate 343a, 343b, and the plate internal flow path 347. Therefore, the cooling oil supplied to the plate internal flow path 347 (see Fig.12 The arrow Y10 in the figure supplies the flow path 38 in the core of each rotor core 30a, 30b (see Fig.12 Y11 in the figure).

[0173] Next, based on Fig.13 The effect of the oil passing plate 331 when the rotor 314 rotates will be described.

[0174] Fig.13 It is a cross-sectional view along the axial direction of the refrigerant adjustment unit 344 when the rotor 314 rotates.

[0175] like Fig.13As shown, when the rotor 314 rotates, centrifugal force acts on the slide valve 70, and the slide valve 70 moves radially outward against the elastic force of the coil spring 361. The radially outer end 70b of the slide valve 70 abuts against the stopper 71, and the radially outer movement of the slide valve 70 is restricted.

[0176] In this state, the position of the side communication hole 75 of the slide valve 70 and the position of the communication port 352 of each plate 343a, 343b are offset in the radial direction so that they do not partially overlap when viewed from the axial direction. As a result, the through hole 73 of the slide valve 70 and the communication port 352 of each plate 343a, 343b are cut off. Therefore, the supply of the cooling oil supplied to the plate internal flow path 347 to the core internal flow path 38 of each rotor core 30a, 30b is cut off.

[0177] Therefore, according to the third embodiment described above, it is possible to achieve the same effects as those of the first embodiment described above.

[0178] It should be noted that in the third embodiment described above, the shape of the peripheral surface of the communication passage 364 and the slide valve 70 is a polygonal shape and the rotation of the slide valve 70 relative to the communication passage 364 around the axis J2 is restricted. However, the present invention is not limited to this, and the shape of the peripheral surface of the communication passage 364 and the slide valve 70 can be any shape as long as the rotation of the slide valve 70 relative to the communication passage 364 around the axis J2 can be restricted. For example, a key fitting may be performed to restrict the rotation of the slide valve 70 relative to the communication passage 364 around the axis J2.

[0179] In the third embodiment described above, the stopper 71 is provided so that the position of the side communication hole 75 of the slide valve 70 and the position of the communication port 352 of each plate 343a, 343b are offset in the radial direction when the radial outer end 70b of the slide valve 70 abuts against the stopper 71. The case where the side communication hole 75 and the communication port 352 do not partially overlap when viewed from the axial direction in this offset state is described. However, the present invention is not limited to this, and the side communication hole 75 and the communication port 352 may be partially overlapped when viewed from the axial direction when the radial outer end 70b of the slide valve 70 abuts against the stopper 71. With such a configuration, the flow rate of the cooling oil supplied to the core inner flow path 38 can also be reduced.

[0180] The present invention is not limited to the above-described embodiment, and includes various modifications made to the above-described embodiment without departing from the gist of the present invention.

[0181] For example, in the above-mentioned embodiment, the case where the above-mentioned refrigerant adjustment unit 44, 244, 344 is provided in the motor 10 for driving the vehicle provided in the power unit 1 is described. However, the present invention is not limited thereto, and the structure of the above-mentioned refrigerant adjustment unit 44, 244, 344 can be used for cooling various motors.

[0182] In the above-mentioned embodiment, the case where four refrigerant adjustment parts 44, 244, 344 are provided at equal intervals in the circumferential direction on the oil passing plate 31, 231, 331 is described. However, the present invention is not limited thereto, and at least one refrigerant adjustment part may be provided, and five or more refrigerant adjustment parts may be provided as long as they are connected to the inner core flow path 38 formed in each rotor core 30a, 30b.

[0183] In the above embodiment, the flux barrier (first flux barrier 37) of each rotor core 30a, 30b is used as the inner core flow path 38 for cooling oil to flow. However, the present invention is not limited to this, and the flux barrier and the inner core flow path 38 may be provided separately.

[0184] In the above-mentioned embodiment, the case where the leaf spring 50, the coil spring 61, and the slide valve 70 are provided as the elastic deformation part in the refrigerant adjustment part 44, 244, and 344, and the weight 51, the valve 63, and the slide valve 70 that elastically deform the elastic deformation part by centrifugal force are provided are described. In addition, the case where the flow rate of the cooling oil supplied to the inner flow path 38 of each rotor core 30a and 30b is adjusted by elastically deforming the leaf spring 50 and the coil spring 61 and the slide valve 70 is described. Specifically, the case where the flow rate of the cooling oil supplied to the inner flow path 38 of the core is adjusted in a manner of reducing the flow rate of the cooling oil supplied to the inner flow path 38 when the rotor 14, 214, and 314 (rotor body 17, 217, and 317) rotates is described.

[0185] However, the present invention is not limited thereto, and the refrigerant adjustment unit 44, 244, 344 may be adjusted so as to reduce the flow rate of the cooling oil supplied from the refrigerant supply unit 16b to the inner flow path 38 of each rotor core 30a, 30b as the rotation speed of the rotor 14, 214, 314 (rotor body 17, 217, 317) increases. For example, an electronic control or an electronic valve may be used as the refrigerant adjustment unit.

[0186] In the above embodiment, the power unit 1 is described as including the speed reduction mechanism 2 for reducing the rotation of the rotor 14, 214, 314. However, the invention is not limited to the speed reduction mechanism 2, and any mechanism for changing the rotation speed of the rotor 14, 214, 314 (including speed increase) may be used.

Claims

1. A rotor, wherein: The rotor has: a rotor shaft that rotates about an axis of rotation; and a rotor body which is fitted and fixed to the rotor shaft and rotates integrally with the rotor shaft; The rotor shaft has: a refrigerant flow path formed in the rotor shaft along the rotation axis and through which refrigerant flows; and a refrigerant supply portion that connects the refrigerant flow path to the outer peripheral surface of the rotor shaft, The rotor body has: a first flow path formed in the rotor body along a radial direction intersecting the rotation axis and communicating with the refrigerant supply portion; and a second flow path branched from the first flow path so as to extend along the rotation axis, A refrigerant adjustment unit is provided in the first flow passage, and the refrigerant adjustment unit adjusts the flow rate of the refrigerant supplied from the refrigerant supply unit to the second flow passage so as to decrease as the rotation speed of the rotor body increases.

2. The rotor according to claim 1, wherein: The refrigerant adjustment unit includes an elastic deformation unit. The elastic deformation portion is adjusted to reduce a flow rate of the refrigerant supplied to the second flow path by being elastically deformed by a centrifugal force generated by the rotation of the rotor body.

3. The rotor according to claim 2, wherein: The elastic deformation portion is a spring.

4. The rotor according to claim 3, wherein: The refrigerant adjustment unit includes: a valve configured to be movable along the first flow path; a communication passage that connects the second flow passage with the first flow passage, and opens and closes a first communication port that connects to the first flow passage by movement of the valve; as well as a recessed portion provided between the communication passage and the first flow passage and provided at a position closer to the refrigerant supply portion than the valve, and the recessed portion is provided in a manner that the communication passage is connected to the first flow passage and accommodates the valve, The elastic deformation portion urges the valve toward the recessed portion.

5. The rotor according to claim 4, wherein: In the recessed portion, a cutout portion is formed on an inner side surface in a biasing direction of the elastic deformation portion, and the cutout portion connects an upstream side and a downstream side of the refrigerant in the recessed portion when the valve is in contact with the inner side surface.

6. The rotor according to claim 3, wherein: The refrigerant adjustment unit includes: a slide valve, which is arranged to be movable along the first flow path and is formed with a through hole capable of connecting the first flow path with the second flow path; a first stopper which limits movement of the slide valve toward the refrigerant supply portion at a position where the through hole communicates with the second flow path; as well as a second stopper for restricting movement of the slide valve to a side opposite to the refrigerant supply portion at a position where communication between the through hole and the second flow path is cut off; The elastic deformation portion urges the slide valve toward the first stopper.

7. The rotor according to claim 3, wherein: The elastic deformation portion is a leaf spring extending in the radial direction for opening and closing the second communication port communicating with the second flow path. The elastic deformation portion comprises: a counterweight disposed at the radially outer end of the elastic deformation portion; and a fixing portion, which is provided at the radial inner end of the elastic deformation portion and fixes the elastic deformation portion to the first flow path, The elastic deformation portion is inclined so as to be separated from the second communication port as it moves from the fixing portion toward the outer side in the radial direction in a state where no centrifugal force generated by the rotation of the rotor body acts.

8. The rotor according to claim 7, wherein: The elastic deformation portion includes a hole portion whose diameter is formed smaller than the inner diameter of the second communication port.

9. A rotating electrical machine, wherein: The rotating electrical machine comprises: The rotor according to any one of claims 1 to 8; and The stator is formed so as to surround the outer circumference of the rotor and generates a magnetic field for applying a rotational force to the rotor.

10. The rotating electrical machine according to claim 9, wherein: The rotating electric machine includes at least one of a transmission for changing the speed of the rotation of the rotor and outputting the rotation, and a drive transmission unit for transmitting the rotation of the rotor to an axle. The rotor shaft includes a transmission coolant supply portion that supplies the coolant to at least one of the transmission and the drive transmission portion.

Images