CN111446795A - Rotor and shaft manufacturing method - Google Patents
Rotor and shaft manufacturing method Download PDFInfo
- Publication number
- CN111446795A CN111446795A CN202010011404.6A CN202010011404A CN111446795A CN 111446795 A CN111446795 A CN 111446795A CN 202010011404 A CN202010011404 A CN 202010011404A CN 111446795 A CN111446795 A CN 111446795A
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- Prior art keywords
- refrigerant
- shaft
- rotor
- axial
- passage
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K1/00—Details of the magnetic circuit
- H02K1/06—Details of the magnetic circuit characterised by the shape, form or construction
- H02K1/22—Rotating parts of the magnetic circuit
- H02K1/32—Rotating parts of the magnetic circuit with channels or ducts for flow of cooling medium
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K9/00—Arrangements for cooling or ventilating
- H02K9/19—Arrangements for cooling or ventilating for machines with closed casing and closed-circuit cooling using a liquid cooling medium, e.g. oil
- H02K9/197—Arrangements for cooling or ventilating for machines with closed casing and closed-circuit cooling using a liquid cooling medium, e.g. oil in which the rotor or stator space is fluid-tight, e.g. to provide for different cooling media for rotor and stator
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/64—Electric machine technologies in electromobility
Abstract
The invention provides a rotor and a method for manufacturing a shaft used for the rotor, wherein the unbalance of the shaft during rotation is restrained and the cooling efficiency is improved. The shaft (3) has an axial refrigerant path (31), and the axial refrigerant path (31) is concentrically disposed in the shaft (3) and circulates a refrigerant (S) for cooling the rotor core (2). The axial refrigerant passage (31) has tapered surfaces formed so that the refrigerant flow area is minimized at both ends of the shaft (3) and increases as the refrigerant flow area moves from both ends of the shaft (3) toward the center in the axial direction.
Description
Technical Field
The present invention relates to a rotor and a shaft manufacturing method.
Background
Conventionally, a rotating electrical machine has been used as a power source for hybrid vehicles and electric vehicles. In a rotating electrical machine, magnetic attraction or repulsion is generated between a magnet provided in a rotor core and a stator around which a coil is wound. Thereby, the rotor rotates relative to the stator.
However, the rotor generates heat by the influence of eddy currents or the like generated in the magnet when rotating. If the magnetic force decreases due to heat generation of the magnet (so-called thermal demagnetization), the performance of the rotating electric machine may decrease. Also, if a current flows in the coil of the stator, the coil generates heat due to copper loss. The heat generation of the coil is a factor that degrades the performance of the rotating electric machine. Therefore, various techniques have been proposed for cooling the rotor and the coil by supplying a refrigerant to the rotor and the coil during rotation.
For example, patent document 1 (japanese patent application laid-open No. 9-154258) describes a structure in which the inside of a rotor rotation shaft is hollow, and cooling oil is sent from the outside to the pressure and is scattered by centrifugal force to cool a coil. In patent document 1, the rotor rotating shaft is made hollow and tapered, and the cooling oil pressure feed port side is made small and the output shaft side is made large.
Disclosure of Invention
Summary of The Invention
Problems to be solved by the invention
However, in the technique described in patent document 1, since the inside of the rotating shaft is formed in a tapered shape only on one side in the axial direction, unbalance of the shaft occurs, and the shaft becomes a cause of the runout (れ - り) on one side in the axial direction. This may cause vibration when the rotor rotates, and may degrade rotor performance. In addition, when the coolant is supplied from the axial rotor core, the cooling efficiency may be reduced due to the uneven supply amount of the coolant and the limited supply direction of the coolant to the shaft.
Accordingly, an object of the present invention is to provide a rotor in which cooling efficiency is improved by suppressing unbalance of a shaft during rotation, and a method for manufacturing a shaft used for the rotor.
Means for solving the problems
A rotor (for example, a rotor 1 according to a first embodiment) according to an aspect of the present invention includes a rotor core (for example, a rotor core 2 according to a first embodiment) and a shaft (for example, a shaft 3 according to a first embodiment) that supports the rotor core, the shaft including an axial refrigerant passage (for example, an axial refrigerant passage 31 according to a first embodiment) that is provided concentrically with the shaft and through which a refrigerant (for example, a refrigerant S according to a first embodiment) for cooling the rotor core flows, the axial refrigerant passage having a maximum refrigerant flow area at a central portion in an axial direction of the shaft.
The rotor may include a rotor core and a shaft that supports the rotor core, the shaft may include an axial refrigerant passage that is provided concentrically with the shaft and through which a refrigerant for cooling the rotor core flows, and the axial refrigerant passage may have a shape that allows the refrigerant supplied to the axial refrigerant passage to approach a central portion of the shaft in an axial direction.
The rotor may have a tapered surface (for example, the tapered surface 53 in the first embodiment) in which the axial refrigerant passage has a minimum refrigerant flow area at both end portions of the shaft and the refrigerant flow area increases from the both end portions of the shaft toward the center portion.
The rotor may further include a pair of refrigerant supply pipes (for example, the refrigerant supply pipe 4 in the first embodiment) that are disposed radially inward of the axial refrigerant passage and that supply the refrigerant from both ends of the shaft to the axial refrigerant passage.
The rotor may further include a refrigerant supply pipe (for example, the refrigerant supply pipe 204 in the second embodiment) concentrically provided in the shaft, arranged radially inside the axial refrigerant passage, and extending between both end portions of the shaft, the refrigerant supply pipe flowing the refrigerant from one end portion (for example, the one end portion 245 in the second embodiment) of the refrigerant supply pipe in the extending direction toward the other end portion (for example, the other end portion 246 in the second embodiment) of the refrigerant supply pipe, the refrigerant supply pipe having a refrigerant supply hole (for example, the refrigerant supply hole 242 in the second embodiment) for supplying the refrigerant to the axial refrigerant passage.
In the rotor, the axial refrigerant passage may have a minimum refrigerant flow area at both end portions of the shaft, and a tapered surface that increases the refrigerant flow area from both end portions of the shaft toward the center portion, the shaft may further have a radial refrigerant passage (for example, the radial refrigerant passage 32 in the first embodiment) that communicates with the axial refrigerant passage and penetrates the shaft in the radial direction, and the refrigerant supply hole may be spaced apart from the center portion in the axial direction as compared to the radial refrigerant passage.
Further, the rotor may be configured such that the shaft further includes a radial refrigerant passage communicating with the axial refrigerant passage and penetrating the shaft in the radial direction, and the rotor further includes a supply pipe side guide wall (for example, a supply pipe side guide wall 343 in the third embodiment) projecting radially outward from an outer periphery of the refrigerant supply pipe and guiding the refrigerant such that the refrigerant from the refrigerant supply hole is supplied to a position separated from the center portion in the axial direction from the radial refrigerant passage.
Further, the rotor may be configured such that the shaft further includes a radial refrigerant passage communicating with the axial refrigerant passage and penetrating the shaft in the radial direction, and the rotor further includes a refrigerant-side guide wall (for example, a refrigerant-side guide wall 433 in the fourth embodiment) that protrudes radially inward from an inner periphery of the axial refrigerant passage and guides the refrigerant so that the refrigerant from the refrigerant supply hole is supplied to the target radial refrigerant passage.
In addition, a shaft manufacturing method according to an aspect of the present invention includes: a first step of producing a first member (for example, a first member 40 according to a first embodiment) having: a pair of recesses (for example, recesses 41 in the first embodiment) that are recessed from both ends of a cylindrical member in the axial direction toward the inside in the axial direction and are concentric with the cylindrical member; and a partition wall (e.g., the partition wall 42 in the first embodiment) located between the pair of recesses in the axial direction; a second step of forming a through hole having an opening area smaller than that of the recess and concentric with the cylindrical member in the partition wall after the first step, thereby forming a step (for example, the step 43 in the first embodiment) in the center portion in the axial direction of the first member; a third step of producing a pair of second members (for example, the second members 50 in the first embodiment) having a smallest refrigerant flow area at a first end (for example, the first end 51 in the first embodiment) and having a tapered surface that increases as going from the first end toward a second end (for example, the second end 52 in the first embodiment); and a fourth step of press-fitting the pair of second members into the pair of recesses of the first member, respectively, so that the second end portions of the pair of second members are brought into contact with the step portions, respectively, thereby producing a shaft having the largest refrigerant flow area at the center portion in the axial direction.
Effects of the invention
According to the rotor according to the aspect of the present invention, since the refrigerant flow area of the refrigerant passage provided in the axial center of the shaft is maximized at the center portion in the axial direction of the shaft, the shape of the shaft can be made symmetrical about the center portion as compared with the conventional art having the largest diameter at one side in the axial direction of the shaft. This can suppress unbalance of the shaft.
Further, since the axial center refrigerant passage has the largest diameter at the center portion, the refrigerant can be supplied from both end portions of the shaft. The refrigerant supplied from both end portions of the shaft moves toward the center portion of the shaft by a centrifugal force during rotation. This increases the flow velocity of the refrigerant flowing through the shaft, thereby improving the cooling efficiency.
Therefore, a rotor in which unbalance of the shaft during rotation is suppressed and cooling efficiency is improved can be provided.
According to the rotor, for example, the refrigerant supplied to the axial refrigerant passage can be brought close to the center of the shaft by the axial refrigerant passage. This increases the flow velocity of the refrigerant supplied from both ends of the shaft, and makes the flow of the refrigerant uniform toward the center. This can suppress unbalance of the shaft.
Further, since the refrigerant can be collected to the center portion of the shaft, the refrigerant can be supplied from the center portion in the axial direction to the rotor internal flow passage formed inside the rotor core. This makes it possible to make the flow of the refrigerant inside the rotor core uniform, thereby improving the cooling efficiency of the rotor core.
Therefore, a rotor in which unbalance of the shaft during rotation is suppressed and cooling efficiency is improved can be provided.
According to the above rotor, for example, the axial refrigerant passage has a tapered surface, and therefore the refrigerant supplied from both end portions of the shaft flows in the axial refrigerant passage along the tapered surface and moves to the central portion. This enables the refrigerant in the axial refrigerant passage to stably move, thereby improving the cooling efficiency of the rotor.
According to the rotor, the refrigerant is supplied from both end portions of the shaft to the axial refrigerant passage through the refrigerant supply pipe, for example. This can suppress unbalance of the shaft due to deviation of the amount of refrigerant flowing inside the shaft. The refrigerant moves from both end portions of the shaft toward the center portion, and can be supplied from the center portion of the shaft to the rotor internal flow path. This makes it possible to make the flow of the refrigerant inside the rotor core uniform, thereby improving the cooling efficiency of the rotor core. Further, the flow of the refrigerant flowing through the axial center refrigerant passage can be stabilized even when the axial length of the shaft is long. This can provide a rotor with improved cooling efficiency.
According to the above rotor, for example, since the refrigerant supply pipe has the refrigerant supply hole, the refrigerant flowing through the refrigerant supply pipe is supplied from the refrigerant supply hole to the axial refrigerant passage. Thus, even in a configuration in which the refrigerant is supplied from one side in the axial direction of the shaft, the amount of the refrigerant supplied to the axial center refrigerant passage can be made uniform. This can improve the degree of freedom in designing a refrigerant supply method and the like.
According to the above rotor, for example, the refrigerant supply hole is provided at a position axially farther from the center portion than the radial refrigerant path. Thereby, the refrigerant discharged from the refrigerant supply hole moves toward the center in the axial direction along the tapered surface of the axial refrigerant passage, and is supplied to the radial refrigerant passage. This enables the refrigerant to be reliably supplied to the target radial refrigerant passage. Further, since the refrigerant supply hole may be provided between the target radial refrigerant passage and the radial refrigerant passage adjacent to the target radial refrigerant passage in the direction away from the central portion, the labor and time required for manufacturing the refrigerant supply hole can be reduced as compared with the case where the refrigerant supply hole is formed directly above the target radial refrigerant passage. This makes it possible to provide a rotor having excellent workability.
In addition, when a plurality of radial refrigerant passages are formed in the axial direction, the amount of refrigerant supplied to each radial refrigerant passage can be set to a desired amount by changing the size of the refrigerant supply hole corresponding to each radial refrigerant passage. This makes it possible to provide a rotor having an improved degree of freedom in design and improved cooling efficiency.
According to the above rotor, for example, since the refrigerant supply pipe has the supply pipe side guide wall, the refrigerant discharged from the refrigerant supply hole is supplied to the axial refrigerant passage along the supply pipe side guide wall. This enables more accurate supply of the refrigerant to the target radial refrigerant passage. This makes it possible to precisely control the distribution amount of the refrigerant to the flow path inside the rotor, thereby further improving the cooling efficiency of the rotor.
According to the above rotor, for example, the shaft has the refrigerant-side guide wall, and therefore the refrigerant discharged from the refrigerant supply hole is supplied to the radial refrigerant path along the refrigerant-side guide wall. This enables more accurate supply of the refrigerant to the target radial refrigerant passage. This makes it possible to precisely control the distribution amount of the refrigerant to the flow path inside the rotor, thereby further improving the cooling efficiency of the rotor.
A method of manufacturing a shaft according to one aspect of the present invention includes a first step, a second step, a third step, and a fourth step. In the first step, a first member having a pair of recesses formed with a partition wall interposed therebetween is produced. In the second step, a through hole is formed in the partition wall. In the third step, a pair of third members having tapered surfaces is produced. In the fourth step, the pair of third members are press-fitted into the pair of recesses of the second member, respectively, to produce the shaft. In this way, the two members, the second member and the third member, which are easy to manufacture, are combined to manufacture the shaft, so that the workability of manufacturing the shaft can be improved.
Further, since the shaft has the largest refrigerant flow area at the center portion in the axial direction, the shape of the shaft can be made symmetrical about the center portion. This can suppress unbalance of the shaft. Further, since the refrigerant supplied to the shaft moves along the tapered surface toward the center of the shaft, the flow velocity of the refrigerant flowing inside the shaft can be increased, and the cooling efficiency can be improved.
Therefore, it is possible to provide a shaft in which unbalance of the shaft at the time of rotation is suppressed and cooling efficiency is improved.
Drawings
Fig. 1 is a sectional view showing a schematic configuration of a rotating electric machine according to a first embodiment.
Fig. 2 is a sectional view of the shaft and the refrigerant supply pipe according to the first embodiment.
Fig. 3 is a sectional view of the shaft of the first embodiment.
Fig. 4 is a sectional view of the first member of the first embodiment.
Fig. 5 is a sectional view of the second member of the first embodiment.
Fig. 6 is a sectional view of a shaft and a refrigerant supply pipe according to the second embodiment.
Fig. 7 is a sectional view of a shaft and a refrigerant supply pipe according to the third embodiment.
Fig. 8 is a sectional view of a shaft and a refrigerant supply pipe according to the fourth embodiment.
Fig. 9 is a sectional view of a shaft of a first modification.
Fig. 10 is a sectional view of a shaft of a second modification.
Fig. 11 is a sectional view of a shaft of a third modification.
Description of the reference numerals
1 rotor
2 rotor core
3. 403 shaft
4. 204, 304 refrigerant supply pipe
31 axial refrigerant path
32 radial refrigerant path
40 first member
41 recess
42 partition wall
43 step part
50 second member
51 first end part
52 second end portion
53 conical surface
242 refrigerant supply hole
245 one side end portion
246 other end portion
343 feed pipe side guide wall
433 refrigerant road side guide wall
S refrigerant
Detailed Description
Hereinafter, embodiments of the present invention will be described with reference to the drawings.
(first embodiment)
(rotating electric machine)
Fig. 1 is a sectional view showing a schematic configuration of a rotating electric machine 10 according to an embodiment.
The rotating electrical machine 10 shown in fig. 1 is a traveling electric motor mounted on a vehicle such as a hybrid vehicle or an electric vehicle. However, the configuration of the present invention is not limited to the electric motor for running, and may be applied to an electric motor for power generation, an electric motor for other applications, and a rotating electric machine (including a generator) other than a vehicle.
The rotating electric machine 10 includes a stator 6 and a rotor 1.
The stator 6 includes a stator core 7 and a coil 8 attached to the stator core 7.
The stator core 7 is cylindrical and disposed coaxially with the axis C. In the following description, a direction along the axis C of the stator core 7 is simply referred to as an axial direction, a direction perpendicular to the axis C is referred to as a radial direction, and a direction around the axis C is referred to as a circumferential direction. The stator core 7 is formed by laminating electromagnetic steel sheets in the axial direction. The stator core 7 may be a so-called dust core obtained by compression molding metal magnetic powder (soft magnetic powder). The stator core 7 is fixed to an inner peripheral surface of a casing, not shown.
The coil 8 is fitted to the stator core 7. The coil 8 includes a U-phase coil, a V-phase coil, and a W-phase coil arranged with a predetermined phase difference in the circumferential direction. The coil 8 includes an insertion portion 8a inserted into an insertion slot (not shown) of the stator core 7 and a coil end 8b protruding from the stator core 7 in the axial direction. A magnetic field is generated in the stator core 7 by the current flowing through the coil 8.
(rotor)
The rotor 1 is disposed radially inward of the stator 6. The rotor 1 includes a rotor core 2, a shaft 3, and a refrigerant supply pipe 4 (see fig. 2).
(rotor core)
The rotor core 2 is disposed radially inward of the stator 6 with a gap therebetween. The rotor core 2 is formed in a cylindrical shape disposed coaxially with the axis C. A shaft through hole 21 is formed in a radial center portion of the rotor core 2 to axially penetrate the rotor core 2. The shaft 3 is fixed to the shaft through hole 21 by press fitting or the like. Thereby, the rotor core 2 is axially supported by the shaft 3 and can rotate integrally with the shaft 3 about the axis C.
A magnet holding hole 22 is formed in the outer peripheral portion of the rotor core 2 to axially penetrate the rotor core 2. The magnet holding holes 22 are formed in plurality at intervals in the circumferential direction. The magnet 11 is inserted into each magnet holding hole 22.
The magnet 11 is, for example, a rare-earth magnet. Examples of the rare-earth magnet include neodymium magnet, samarium-cobalt magnet, and praseodymium magnet.
The rotor core 2 has a rotor internal flow path 23 between the magnet holding hole 22 and the shaft through hole 21 in the radial direction. The rotor internal flow path 23 includes a communication hole 24 and a core connection path 25.
The communication hole 24 is formed radially inward of the magnet holding hole 22 and radially outward of the shaft through hole 21. The communication hole 24 axially penetrates the rotor core 2. The communication hole 24 is formed in plurality in the circumferential direction.
The core connecting passage 25 is provided at the center in the axial direction of the rotor core 2. The core connecting passage 25 extends in the radial direction between the communication hole 24 and the shaft through hole 21. The communication hole 24 is connected to the shaft through hole 21 through the core connection passage 25. The core connecting passages 25 are formed in plural numbers (the same number as the communication holes 24) in the circumferential direction.
(axle)
The shaft 3 is press-fitted and fixed to the shaft through hole 21 of the rotor core 2. The shaft 3 is disposed coaxially with the axis C. The shaft 3 is formed in a cylindrical shape having a hollow interior. The shaft 3 includes a shaft center refrigerant passage 31 and a radial refrigerant passage 32.
The axial refrigerant passage 31 is concentrically provided in the shaft 3. The coolant S for cooling the rotor core 2 can flow through the axial coolant passage 31. The axial refrigerant passage 31 has a minimum refrigerant flow area at both ends of the shaft 3 and is formed with tapered surfaces that increase in refrigerant flow area from both ends of the shaft 3 toward the center in the axial direction. The axial refrigerant passage 31 has the largest refrigerant flow area at the center portion in the axial direction of the shaft 3. In the present embodiment, the axial refrigerant passage 31 is formed in a circular cross-sectional shape when viewed from the axial direction.
The radial refrigerant passage 32 is provided in the center of the shaft 3 in the axial direction. The radial refrigerant passage 32 radially penetrates the shaft 3. The plurality of radial refrigerant passages 32 are formed in the circumferential direction. The radial refrigerant passage 32 communicates the axial refrigerant passage 31 with the outer peripheral portion of the shaft 3. The radially outer side of the radial refrigerant passage 32 communicates with the radially inner side of the core connecting passage 25 of the rotor core 2. Thus, the refrigerant S supplied to the axial refrigerant passage 31 can flow into the rotor internal flow passage 23 of the rotor core 2 through the radial refrigerant passage 32.
(refrigerant supply pipe)
Fig. 2 is a sectional view of the shaft 3 and the refrigerant supply pipe 4.
As shown in fig. 2, the refrigerant supply pipe 4 is provided in a pair at both end portions of the shaft 3. The refrigerant supply pipe 4 is disposed radially inward of the axial refrigerant passage 31. The refrigerant S conveyed by a pump, not shown, through the refrigerant supply pipe 4 is supplied from both ends of the shaft 3 to the axial refrigerant passage 31.
Fig. 3 is a sectional view of the shaft 3.
As shown in fig. 3, the shaft 3 has a first member 40 and a pair of second members 50.
Fig. 4 is a sectional view showing the first member 40 of the shaft 3. Fig. 5 is a sectional view showing the second member 50 of the shaft 3.
Next, a method for manufacturing the shaft 3 will be described.
The shaft manufacturing method includes a first step, a second step, a third step, and a fourth step.
As shown in fig. 4, in the first step, a first member 40 is produced, and the first member 40 includes: a pair of recesses 41 recessed from both ends of the cylindrical member in the axial direction toward the inside in the axial direction and concentric with the cylindrical member; and a partition wall 42 located between the pair of recesses 41 in the axial direction. The first member 40 is formed by, for example, a metal material. The first member 40 is formed in a cylindrical shape.
In the second step, a through hole having an opening area smaller than that of the recess 41 of the first member 40 and concentric with the cylindrical member is formed in the partition wall 42, whereby a stepped portion 43 is formed in the center portion of the first member 40 in the axial direction. Further, a radial refrigerant passage 32 is formed to penetrate the step portion 43 in the radial direction.
As shown in fig. 5, in the third step, the second member 50 having the smallest refrigerant flow area at the first end 51 and having the tapered surface 53 is produced, and the refrigerant flow area of the tapered surface 53 increases from the first end 51 toward the second end 52. In the third step, a pair of second members 50 is produced (only one of the second members 50 is shown in fig. 5). The second member 50 is formed by, for example, a resin material. The second member 50 is formed in a cylindrical shape.
As shown in fig. 3, in the fourth step, the pair of second members 50 are press-fitted into the pair of recesses 41 of the first member 40, and the second end portions 52 of the pair of second members 50 are brought into contact with the step portions 43, respectively, to produce the shaft 3 having the largest refrigerant flow area at the center portion in the axial direction.
In this way, the shaft 3 is formed through the first to fourth steps.
Next, the operation of the rotor 1 will be described.
As shown in fig. 2, the refrigerant S is supplied from the refrigerant supply pipe 4 to the axial refrigerant passage 31. When the rotor rotates, a force directed radially outward by a centrifugal force acts on the refrigerant S. Since the tapered surface 53 is formed inside the shaft 3, the refrigerant S moves from both end portions in the axial direction toward the center portion along the tapered surface 53. Then, the refrigerant S moved to the center of the axial refrigerant passage 31 is supplied to the radial refrigerant passage 32 by centrifugal force. The refrigerant S passes through the radial refrigerant passage 32 and is supplied to the rotor internal flow passage 23 (see fig. 1). Specifically, as shown in fig. 1, the refrigerant S moves in the order of the radial refrigerant passage 32, the core connection passage 25 communicating with the radial refrigerant passage 32, and the communication hole 24, and is discharged from the end face of the rotor core 2 to the outside of the rotor 1. In this way, the coolant S moves inside the rotor core 2, thereby cooling the rotor core 2.
The refrigerant S flowing through the rotor internal flow path 23 is discharged from the end face of the rotor core 2 to the outside of the rotor 1. The discharged refrigerant S is scattered toward the coil end 8b of the stator 6, and the refrigerant S is supplied to the coil end 8 b. Thereby, the coil 8 is cooled.
In this way, the coolant S moves in the order of the coolant supply pipe 4, the axial coolant path 31, the radial coolant path 32, the core connection path 25, and the communication hole 24, and cools the rotor 1. The stator 6 is cooled by the refrigerant S discharged from the rotor 1.
(action, Effect)
According to rotor 1 of the present embodiment, since the refrigerant flow area of axial refrigerant passage 31 provided in shaft 3 is maximized at the center portion in the axial direction of shaft 3, the shape of shaft 3 can be made symmetrical about the center portion as compared with the conventional art having the largest diameter at one side in the axial direction of shaft 3. This can suppress unbalance of the shaft 3.
Further, since the axial center refrigerant passage 31 has the largest diameter at the center portion, the refrigerant S can be supplied from both end portions of the shaft 3. The refrigerant S supplied from both end portions of the shaft 3 moves toward the center portion of the shaft 3 by a centrifugal force during rotation. This increases the flow velocity of the refrigerant S flowing through the shaft 3, thereby improving the cooling efficiency.
Therefore, the rotor 1 in which the unbalance of the shaft 3 during rotation is suppressed and the cooling efficiency is improved can be provided.
Here, in the case of a configuration in which the refrigerant S is supplied from the axial refrigerant passage 31 of the shaft 3 to the rotor internal passage 23 formed inside the rotor core 2, the refrigerant S is preferably supplied from the center portion in the axial direction of the rotor core 2. According to the configuration of the present invention, the refrigerant S supplied from the center portion of the axial refrigerant passage 31 to the rotor internal passage 23 moves from the center portion toward both ends in the axial direction in the rotor internal passage 23, and is then discharged from the rotor core 2 and supplied to the coil end 8 b. Thereby, the coil 8 is cooled. This suppresses the deviation of the refrigerant S flowing through the rotor internal flow path 23 to stabilize the flow of the refrigerant, thereby improving the cooling efficiency of the rotor 1 and the coil end 8 b.
Further, the axial refrigerant passage 31 can make the refrigerant S supplied to the axial refrigerant passage 31 closer to the center portion in the axial direction of the shaft 3. This increases the flow velocity of the refrigerant S supplied from both end portions of the shaft 3, and makes the flow of the refrigerant S uniform toward the center portion. This can suppress unbalance of the shaft 3.
Further, since the refrigerant S can be collected in the central portion of the shaft 3, the refrigerant S can be supplied from the central portion in the axial direction to the rotor internal flow passage 23 formed inside the rotor core 2. This makes it possible to make the flow of the refrigerant inside the rotor core 2 uniform, thereby improving the cooling efficiency of the rotor core 2.
Therefore, the rotor 1 in which the unbalance of the shaft 3 during rotation is suppressed and the cooling efficiency is improved can be provided.
Since the axial refrigerant passage 31 has the tapered surface 53, the refrigerant S supplied from both ends of the shaft 3 flows through the axial refrigerant passage 31 along the tapered surface 53 and moves to the center. This enables the refrigerant S in the axial refrigerant passage 31 to stably move, thereby improving the cooling efficiency of the rotor 1.
Further, the refrigerant S is supplied from both ends of the shaft 3 to the axial refrigerant passage 31 through the refrigerant supply pipe 4. This can suppress unbalance of the shaft 3 due to deviation of the amount of refrigerant flowing inside the shaft 3. The refrigerant S moves from both end portions of the shaft 3 toward the center portion, and can be supplied from the center portion of the shaft 3 to the rotor internal flow path 23. This makes it possible to make the flow of the refrigerant inside the rotor core 2 uniform, thereby improving the cooling efficiency of the rotor core 2. Further, even when the axial length of the shaft 3 is long, the flow of the refrigerant S flowing through the axial center refrigerant passage 31 can be stabilized. This can provide the rotor 1 with improved cooling efficiency.
According to the method for manufacturing the shaft 3 of the present embodiment, the method for manufacturing the shaft 3 includes the first step, the second step, the third step, and the fourth step. In the first step, a first member 40 having a pair of recesses 41 formed with a partition wall 42 interposed therebetween is produced. In the second step, the step portion 43 is formed by forming a through hole in the partition wall 42. In the third step, a pair of second members 50 having tapered surfaces 53 is produced. In the fourth step, the pair of second members 50 is press-fitted into the pair of recesses 41 of the first member 40, respectively, to produce the shaft 3. In this way, since the shaft 3 is produced by combining two members, i.e., the first member 40 and the second member 50, which are easy to produce, the workability of producing the shaft 3 can be improved.
Further, since the shaft 3 has the largest refrigerant flow area at the center portion in the axial direction, the shape of the shaft 3 can be made symmetrical about the center portion. This can suppress unbalance of the shaft 3. Further, since the refrigerant S supplied to the shaft 3 moves toward the center of the shaft 3 along the tapered surface 53, the flow velocity of the refrigerant S flowing inside the shaft 3 can be increased, and the cooling efficiency can be improved.
Therefore, the shaft 3 can be manufactured with improved cooling efficiency while suppressing unbalance of the shaft 3 during rotation.
Next, a second embodiment to a fourth embodiment will be described with reference to fig. 6 to 8. In the second to fourth embodiments, the same members as those in the first embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.
(second embodiment)
A second embodiment of the present invention will be explained. Fig. 6 is a sectional view of the shaft 3 and the refrigerant supply pipe 204 of the second embodiment. In the present embodiment, the refrigerant supply pipe 204 extends between both end portions of the shaft 3, which is different from the above-described embodiment.
In the present embodiment, a plurality of (three in the present embodiment) radial refrigerant passages 32 are formed in the shaft 3 in the axial direction.
The refrigerant supply pipe 204 extends between both end portions of the shaft 3. In the refrigerant supply pipe 204, the refrigerant S flows from one end 245 toward the other end 246 in the extending direction of the refrigerant supply pipe 204. The refrigerant supply pipe 204 has a refrigerant supply hole 242. A plurality of (three in the present embodiment) refrigerant supply holes 242 are provided in the axial direction. The refrigerant supply hole 242 supplies the refrigerant S to the axial refrigerant passage 31. Each of the refrigerant supply holes 242 is provided corresponding to each of the plurality of radial refrigerant passages 32. Specifically, the refrigerant supply hole 242 is provided at a position axially distant from the center portion of the corresponding radial refrigerant passage 32.
According to the present embodiment, since refrigerant supply pipe 204 has refrigerant supply hole 242, refrigerant S flowing through refrigerant supply pipe 204 is supplied from refrigerant supply hole 242 to axial center refrigerant passage 31. Thus, even in the configuration in which the refrigerant S is supplied from one side in the axial direction of the shaft 3, the amount of the refrigerant supplied to the axial center refrigerant passage 31 can be made uniform. This can improve the degree of freedom in designing a refrigerant supply method and the like.
The refrigerant supply hole 242 is provided at a position axially farther from the center than the radial refrigerant passage 32. Thereby, the refrigerant S discharged from the refrigerant supply hole 242 moves along the tapered surface 53 of the axial refrigerant passage 31 toward the center in the axial direction, and is supplied to the radial refrigerant passage 32. This enables the refrigerant S to be reliably supplied to the target radial refrigerant passage 32. Further, since the refrigerant supply hole 242 may be provided between the target radial refrigerant passage 32 and the adjacent radial refrigerant passage 32 in the direction away from the center portion than the target radial refrigerant passage 32, the labor and time required for manufacturing the target radial refrigerant passage 32 can be reduced as compared with the case where the refrigerant supply hole 242 is formed directly above the target radial refrigerant passage 32. This enables the rotor 1 to be excellent in workability.
In the case where a plurality of radial refrigerant passages 32 are formed in the axial direction, the amount of refrigerant supplied to each radial refrigerant passage 32 can be set to a desired amount by changing the size of the refrigerant supply hole 242 corresponding to each radial refrigerant passage 32. This can provide the rotor 1 having an improved degree of freedom in design and improved cooling efficiency.
(third embodiment)
A third embodiment of the present invention will be explained. Fig. 7 is a sectional view of the shaft 3 and the refrigerant supply pipe 304 of the third embodiment. In the present embodiment, the refrigerant supply pipe 304 has a supply pipe side guide wall 343, which is different from the above-described embodiments.
In the present embodiment, the refrigerant supply pipe 304 has a supply pipe side guide wall 343. The feed-pipe-side guide wall 343 is formed in the vicinity of the refrigerant feed hole 242. The supply pipe side guide wall 343 protrudes radially outward from the outer periphery of the refrigerant supply pipe 304. The supply pipe side guide wall 343 guides the refrigerant S so that the refrigerant S from the refrigerant supply hole 242 is supplied to a position axially farther from the center than the target radial refrigerant passage 32.
According to the present embodiment, since the refrigerant supply pipe 304 has the supply pipe side guide wall 343, the refrigerant S discharged from the refrigerant supply hole 242 is supplied to the axial center refrigerant passage 31 along the supply pipe side guide wall 343. This enables the refrigerant S to be supplied more accurately to the target radial refrigerant passage 32. This makes it possible to precisely control the distribution amount of the refrigerant to the rotor internal flow path 23, and further improve the cooling efficiency of the rotor 1.
(fourth embodiment)
A fourth embodiment of the present invention will be explained. Fig. 8 is a sectional view of the shaft 403 and the refrigerant supply pipe 4 of the fourth embodiment. In the present embodiment, shaft 403 has refrigerant-side guide wall 433, which is different from the above-described embodiments.
In the present embodiment, shaft 403 has refrigerant-side guide wall 433. Refrigerant-path-side guide wall 433 is formed in the vicinity of radial refrigerant path 32. The refrigerant-side guide wall 433 protrudes radially inward from the inner periphery of the axial refrigerant passage 31. Refrigerant-side guide wall 433 guides refrigerant S so that refrigerant S from refrigerant supply hole 242 is supplied to target radial refrigerant path 32.
According to the present embodiment, since shaft 403 has refrigerant-side guide wall 433, refrigerant S discharged from refrigerant supply hole 242 is supplied to radial refrigerant passage 32 along refrigerant-side guide wall 433. This enables the refrigerant S to be supplied more accurately to the target radial refrigerant passage 32. This makes it possible to precisely control the distribution amount of the refrigerant to the rotor internal flow passage 23, and further improve the cooling efficiency of the rotor 1.
Although the preferred embodiments of the present invention have been described above, the technical scope of the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the scope of the present invention.
For example, in the above-described embodiment, the configuration in which one of the supply pipe side guide wall 343 and the refrigerant side guide wall 433 is provided has been described, but the present invention is not limited to this. Both the supply pipe side guide wall 343 and the refrigerant side guide wall 433 may be provided.
When a plurality of refrigerant supply holes 242 are formed, the diameters of the refrigerant supply holes 242 may be different from each other, or may be all the same.
For example, in the above-described embodiment, the axial refrigerant passage 31 has a circular cross-sectional shape as viewed in the axial direction, but is not limited thereto. For example, the axial refrigerant passage 31 may have a shape other than a circular cross section, such as an elliptical shape, when viewed in the axial direction.
The shape of the axial refrigerant passage 31 of the shaft 3 may be, for example, a stepped shape as shown in fig. 9 or a wave shape as shown in fig. 10, or may be a combination of a stepped shape and a tapered shape as shown in fig. 11.
The second member 50 constituting the shaft 3 may be formed by a metal material.
In addition, the components in the above-described embodiments may be replaced with known components as appropriate without departing from the scope of the present invention, and the above-described embodiments and modifications may be combined as appropriate.
Claims (9)
1. A rotor is characterized by comprising:
a rotor core; and
a shaft that supports the rotor core,
the shaft has a shaft center refrigerant passage concentrically provided in the shaft and through which a refrigerant for cooling the rotor core flows,
the axial center refrigerant passage has a maximum refrigerant flow area at a central portion in the axial direction of the shaft.
2. A rotor is characterized by comprising:
a rotor core; and
a shaft that supports the rotor core,
the shaft has a shaft center refrigerant passage concentrically provided in the shaft and through which a refrigerant for cooling the rotor core flows,
the axial center refrigerant passage has a shape that enables the refrigerant supplied to the axial center refrigerant passage to approach a center portion in the axial direction of the shaft.
3. The rotor of claim 1 or 2,
the axial refrigerant passage has a minimum refrigerant flow area at both end portions of the shaft, and has tapered surfaces that increase in refrigerant flow area from the both end portions of the shaft toward the center portion.
4. A rotor according to any one of claims 1 to 3,
the rotor further includes a pair of refrigerant supply pipes arranged radially inward of the axial refrigerant passage and configured to supply the refrigerant from both ends of the shaft to the axial refrigerant passage.
5. A rotor according to any one of claims 1 to 3,
the rotor further includes a refrigerant supply pipe concentrically disposed on the shaft, disposed radially inward of the axial refrigerant passage, and extending between both end portions of the shaft,
the refrigerant supply pipe allows the refrigerant to flow from one end of the refrigerant supply pipe in the extending direction to the other end,
the refrigerant supply pipe has a refrigerant supply hole for supplying the refrigerant to the axial refrigerant passage.
6. The rotor of claim 5,
the axial refrigerant passage has a minimum refrigerant flow area at both end portions of the shaft, and has tapered surfaces that increase in refrigerant flow area from the both end portions of the shaft toward the center portion,
the shaft further includes a radial refrigerant passage communicating with the axial refrigerant passage and penetrating the shaft in a radial direction,
the refrigerant supply hole is located farther from the central portion than the radial refrigerant passage in the axial direction.
7. The rotor of claim 5 or 6,
the shaft further includes a radial refrigerant passage communicating with the axial refrigerant passage and penetrating the shaft in a radial direction,
the rotor further includes a supply pipe side guide wall that protrudes radially outward from an outer periphery of the refrigerant supply pipe and guides the refrigerant such that the refrigerant from the refrigerant supply hole is supplied to a position that is farther from the center portion than the radial refrigerant path in the axial direction.
8. The rotor according to any one of claims 5 to 7,
the shaft further includes a radial refrigerant passage communicating with the axial refrigerant passage and penetrating the shaft in a radial direction,
the rotor further includes a refrigerant-side guide wall that protrudes radially inward from an inner periphery of the axial refrigerant path and guides the refrigerant such that the refrigerant from the refrigerant supply hole is supplied to the target radial refrigerant path.
9. A method of manufacturing a shaft, comprising:
a first step of manufacturing a first member having: a pair of concave portions that are recessed from both ends in the axial direction of a cylindrical member toward the inside in the axial direction and are concentric with the cylindrical member; and a partition wall located between the pair of recesses in the axial direction;
a second step of forming a through hole having an opening area smaller than the recess and concentric with the cylindrical member in the partition wall after the first step, thereby forming a step in a central portion of the first member in the axial direction;
a third step of producing a pair of second members having a smallest refrigerant flow area at a first end and having tapered surfaces that increase in refrigerant flow area from the first end toward a second end; and
and a fourth step of press-fitting the pair of second members into the pair of recesses of the first member, respectively, and bringing the second end portions of the pair of second members into contact with the step portions, respectively, thereby producing a shaft having the largest refrigerant flow area at the center portion in the axial direction.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2019-005487 | 2019-01-16 | ||
| JP2019005487A JP2020114151A (en) | 2019-01-16 | 2019-01-16 | Rotor and shaft manufacturing method |
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| Publication Number | Publication Date |
|---|---|
| CN111446795A true CN111446795A (en) | 2020-07-24 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010011404.6A Pending CN111446795A (en) | 2019-01-16 | 2020-01-06 | Rotor and shaft manufacturing method |
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| JP (1) | JP2020114151A (en) |
| CN (1) | CN111446795A (en) |
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| JP2014230393A (en) * | 2013-05-22 | 2014-12-08 | トヨタ自動車株式会社 | Rotary electric machine |
| JP2015089316A (en) * | 2013-11-01 | 2015-05-07 | トヨタ自動車株式会社 | Rotary electric machine |
| CN106257801A (en) * | 2015-06-16 | 2016-12-28 | 丰田自动车株式会社 | The rotor of electric rotating machine |
| CN108475968A (en) * | 2015-11-30 | 2018-08-31 | 蒂森克虏伯普利斯坦技术中心股份公司 | The hollow rotor shaft of assembling with cooling medium distribution member |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH09154258A (en) * | 1995-11-29 | 1997-06-10 | Mitsubishi Heavy Ind Ltd | Forcible oil cooled motor or cooling structure of motor |
| JP3758583B2 (en) * | 2002-02-06 | 2006-03-22 | 日産自動車株式会社 | Rotating body cooling structure |
| DE102014107845B4 (en) * | 2014-06-04 | 2024-02-15 | Thyssenkrupp Presta Teccenter Ag | Oil distribution element |
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2019
- 2019-01-16 JP JP2019005487A patent/JP2020114151A/en active Pending
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| JP2005073351A (en) * | 2003-08-22 | 2005-03-17 | Toyota Motor Corp | Cooling structure of rotating electric machine |
| EP1892512A2 (en) * | 2006-08-24 | 2008-02-27 | AVL List GmbH | Electric drive and load machine for high power test beds |
| CN103296808A (en) * | 2012-02-29 | 2013-09-11 | 丰田自动车株式会社 | Cooling structure of rotor for rotary electric machine, and rotary electric machine |
| JP2014230393A (en) * | 2013-05-22 | 2014-12-08 | トヨタ自動車株式会社 | Rotary electric machine |
| JP2015089316A (en) * | 2013-11-01 | 2015-05-07 | トヨタ自動車株式会社 | Rotary electric machine |
| CN106257801A (en) * | 2015-06-16 | 2016-12-28 | 丰田自动车株式会社 | The rotor of electric rotating machine |
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| JP2020114151A (en) | 2020-07-27 |
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Application publication date: 20200724 |