Manufacturing device and manufacturing method for rotor for rotating electric machine

Abstract

To enable proper control of tightening allowance between a rotor core and a hollow rotor shaft over the whole fitting unit.SOLUTION: A device for manufacturing a rotor for a rotary electric machine is disclosed that includes: a support unit that supports a work including a rotor core and a hollow rotor shaft to form a state in which the rotor shaft is disposed on an inner diameter side of the rotor core; an actuation member that can be disposed in a hollow interior of the rotor shaft, has a cavity unit on a radially inner side, and is displaceable or deformable in a radial direction; an actuation and drive member; positioning means for positioning the actuation member with respect to the rotor shaft so that the actuation member is opposed to or in contact with a formation and pressurizing region in an inner peripheral surface of the rotor shaft in a radial direction; and load applying unit for displacing or deforming the actuation member radially outward while bringing a drive member positioned in the cavity section of the actuation member positioned by the positioning means into contact with a contacted section by applying axial force relative to the drive member.SELECTED DRAWING: Figure 2

Description

[Technical field]

[0001] The present disclosure relates to an apparatus and method for manufacturing a rotor for a rotating electric machine. [Background technology]

[0002] There is known a technique for fitting a rotor shaft into a shaft hole of a rotor core by axially compressing a urethane mandrel inserted into the hollow interior of the hollow rotor shaft with a die and a pad (see, for example, Patent Document 1). [Prior art documents] [Patent documents]

[0003] [Patent Document 1] JP 2019-106797 A Summary of the Invention [Problem to be solved by the invention]

[0004] However, in the above-mentioned conventional technology, a urethane mandrel is used and the amount of expansion of the mandrel is controlled by compressive forces from both axial ends, making it difficult to appropriately control the amount of radial expansion of the mandrel at each axial position. Therefore, in the above-mentioned conventional technology, it is difficult to control the interference between the rotor core and the hollow rotor shaft to a desired interference over the entire fitting portion (the entire molding pressure area).

[0005] Therefore, in one aspect, an object of the present disclosure is to make it possible to appropriately control the interference between a rotor core and a hollow rotor shaft over the entire molding pressure region. [Means for solving the problem]

[0006] According to one aspect, there is provided an apparatus for manufacturing a rotor for a rotating electric machine, comprising: a support portion that supports a workpiece including a rotor core and a hollow rotor shaft and forms a state in which the rotor shaft is disposed on an inner diameter side of the rotor core; an actuating member disposable within the hollow interior of the rotor shaft, the actuating member having a cavity on a radially inner side and capable of being displaced or deformed in a radial direction; a drive member that contacts a contacted portion of the actuating member within the cavity of the actuating member; a positioning means for positioning the operating member with respect to the rotor shaft so that the operating member faces or comes into contact with a molding pressure region on an inner peripheral surface of the rotor shaft in a radial direction; A manufacturing apparatus is provided that includes a load application section that applies an axial force to the driving member located within the hollow portion of the operating member positioned by the positioning means, thereby displacing or deforming the operating member radially outward while bringing the driving member into contact with the contacted portion. Effect of the Invention

[0007] In one aspect, the present disclosure enables appropriate control of the interference between the rotor core and the hollow rotor shaft throughout the entire molding pressure region. [Brief description of the drawings]

[0008] [Figure 1] 1 is a cross-sectional view showing a schematic cross-sectional structure of a motor according to an embodiment; [Diagram 2] FIG. 2 is a cross-sectional view illustrating a rotor manufacturing apparatus. [Diagram 3] FIG. 4 is an exploded perspective view of the pressure molding mechanism as viewed from below. [Figure 4] FIG. 2 is a cross-sectional perspective view of the pressure molding mechanism taken along a plane passing through a reference axis. [Diagram 5] FIG. 4 is a perspective view of the pressure molding mechanism in an assembled state as viewed from below. [Figure 6] 1 is a schematic flowchart showing the flow of the present manufacturing method. [Figure 7] 7A to 7C are cross-sectional views each showing a schematic state in some steps shown in FIG. 6. [Figure 8] 7A to 7C are cross-sectional views each showing a schematic state in some steps shown in FIG. 6. [Figure 9] 7A to 7C are cross-sectional views each showing a schematic state in some steps shown in FIG. 6. [Figure 10] 7A to 7C are cross-sectional views each showing a schematic state in some steps shown in FIG. 6. [Figure 11] 7A to 7C are cross-sectional views each showing a schematic state in some steps shown in FIG. 6. [Figure 12A] FIG. 12 is an enlarged view of a portion Q1 in FIG. [Figure 12B] FIG. 11 is an explanatory diagram showing a state of the cam punch in a molding pressurizing step as viewed from above. [Figure 13] 7A to 7C are cross-sectional views each showing a schematic state in some steps shown in FIG. 6. [Figure 14] 7A to 7C are cross-sectional views each showing a schematic state in some steps shown in FIG. 6. [Figure 15] 11A and 11B are explanatory diagrams of modified examples of the cam punch according to the present embodiment. [Figure 16] 13 is an explanatory diagram of a modified example in which a cam punch rotates around a reference axis. [Figure 17] 13A and 13B are explanatory diagrams of another modified example of the pressure molding mechanism according to the present embodiment. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0009] Each embodiment will be described in detail below with reference to the accompanying drawings. Note that the dimensional ratios in the drawings are merely examples and are not intended to be limiting, and shapes and the like in the drawings may be partially exaggerated for the sake of explanation.

[0010] Fig. 1 is a cross-sectional view that shows a schematic cross-sectional structure of a motor 1 according to an embodiment. In Fig. 1, an X-direction is defined, as well as an X-direction X1 side and an X-direction X2 side.

[0011] 1 shows a rotating shaft 12 of a motor 1. In the following description of the motor 1, the axial direction refers to the direction in which the rotating shaft (center of rotation) 12 of the motor 1 extends, and is parallel to the X direction. Additionally, the radial direction refers to the radial direction centered on the rotating shaft 12. Therefore, the radially outer side refers to the side away from the rotating shaft 12, and the radially inner side refers to the side toward the rotating shaft 12. Additionally, the circumferential direction corresponds to the direction of rotation around the rotating shaft 12.

[0012] The motor 1 may be a motor for driving a vehicle, for example, used in a hybrid vehicle or an electric vehicle, but the motor 1 may also be used for any other purpose.

[0013] The motor 1 is an inner rotor type, and the stator 21 is provided so as to surround the radial outside of the rotor 30. The stator 21 has a stator core 22 whose radial outside is fixed to a stator support portion 10.

[0014] The case 2 forms a space that houses the motor 1. The case 2 includes a stator support portion 10. The stator support portion 10 is joined to a radially outer surface of the stator core 22. The stator support portion 10 may have a flow path through which cooling water passes, and / or may have an oil path. The stator support portion 10 may be formed of two or more pieces of members.

[0015] The stator 21 includes a stator core 22 and a stator coil 29 .

[0016] Although the stator core 22 is formed, for example, from laminated steel plates of a circular magnetic material, in a modified example, the stator core 22 may be formed from a green compact obtained by compressing and solidifying magnetic powder. The stator core 22 may be formed from a split core that is split in the circumferential direction, or may be in a form that is not split in the circumferential direction.

[0017] Stator core 22 is formed with a plurality of teeth that protrude radially inward, and has a stator coil 29 wound thereon.

[0018] The stator coil 29 includes, for example, a U-phase coil, a V-phase coil, and a W-phase coil. The stator coil 29 has slot insertion portions (not shown) that are inserted into slots of the stator core 22, as well as coil ends 29A and 29B that protrude from both sides of the stator core 22 in the axial direction.

[0019] The stator coil 29 may be wound around the stator core 22 by assembling coil pieces (not shown) in the form of segment coils to the stator core 22. A segment coil is a form in which the coils of each phase are divided into units that are easy to assemble (for example, units that are inserted into two slots). The coil pieces are formed, for example, by covering a linear conductor (rectangular wire) having a substantially rectangular cross section with an insulating coating (not shown). The linear conductor is made of copper, but in a modified example, the linear conductor may be made of other conductive materials such as iron.

[0020] The rotor 30 is disposed radially inside the stator 21. The rotor 30 includes a rotor core 32 and a rotor shaft 34. The rotor core 32 is fixed to the radially outside of the rotor shaft 34 and rotates integrally with the rotor shaft 34. The rotor shaft 34 is rotatably supported by the case 2 via bearings 14a and 14b. Specifically, the rotor shaft 34 has an inner peripheral surface supported by the bearing 14a on the X1 side and an outer peripheral surface supported by the bearing 14b on the X2 side. The rotor shaft 34 defines the rotating shaft 12 of the motor 1.

[0021] The shape of the inner circumferential surface of rotor shaft 34 may or may not be rotationally symmetrical about rotation axis 12 when viewed from above. For example, the inner circumferential surface of rotor shaft 34 may be circular or elliptical, or may be polygonal, when viewed from above. Spline teeth, grooves, etc. may be formed on the inner circumferential surface or outer circumferential surface of rotor shaft 34.

[0022] Rotor core 32 is formed, for example, from laminated steel plates of a circular magnetic material. Permanent magnets 321 are inserted inside rotor core 32. The number and arrangement of permanent magnets 321 are optional. In a modified example, rotor core 32 may be formed from a green compact obtained by compressing and solidifying magnetic powder.

[0023] End plates 35A, 35B may be attached to both axial sides of rotor core 32. End plates 35A, 35B may have a function of adjusting imbalance of rotor 30 (a function of eliminating imbalance by cutting or the like) in addition to a support function for supporting rotor core 32.

[0024] As shown in FIG. 1, the rotor shaft 34 has a hollow portion 34A. The hollow portion 34A extends over the entire axial length of the rotor shaft 34. The hollow portion 34A may function as an oil passage. For example, as shown by an arrow R1 in FIG. 1, oil is supplied to the hollow portion 34A from one axial end side, and the oil flows along the radially inner surface of the rotor shaft 34, thereby cooling the rotor core 32 from the radially inner side. In addition, the oil flowing along the radially inner surface of the rotor shaft 34 may be ejected radially outward through oil holes 348, 349 formed at both ends of the rotor shaft 34 (arrows R5, R6) and used to cool the coil ends 29A, 29B.

[0025] When the axial range where the rotor shaft 34 is coupled to the rotor core 32 is defined as the coupled portion, the rotor shaft 34 may have a configuration in which one side of the coupled portion is reduced in diameter. Specifically, as shown in FIG. 1, the rotor shaft 34 has a configuration in which the end on the X2 side is reduced in diameter, while the end on the X1 side is not reduced in diameter. Therefore, the hollow portion 34A has a smaller inner diameter at the end on the X2 side. Specifically, the rotor shaft 34 has a first inner diameter r1 from the end face on the X1 side to the end on the X2 side, and has a second inner diameter r2 at the end on the X2 side. The second inner diameter r2 is significantly smaller than the first inner diameter r1.

[0026] 1, the value of the first inner diameter r1 is substantially constant, and a first step portion 346 for receiving the thrust load of the bearing 14a is formed as a step portion where the value of the first inner diameter r1 changes. Note that the step (radial difference) of the first step portion 346 may be significantly smaller than that of the second radial step portion 347 associated with the change from the first inner diameter r1 to the second inner diameter r2.

[0027] Such rotor shaft 34 has a relatively large first inner diameter r1 in the axial range where it joins with rotor core 32, so that permanent magnets 321 and the like can be efficiently cooled via oil running along the inner circumferential surface of rotor shaft 34.

[0028] 1 shows the motor 1 having a specific structure, the structure of the motor 1 may be substantially arbitrary as long as the hollow rotor shaft 34 is fitted in the axial hole 329 (shaft hole) of the rotor core 32, and the detailed structure of the hollow portion 34A of the rotor shaft 34 may also be arbitrary. Also, while a specific cooling method using oil is disclosed in FIG. 1, the method of cooling the motor 1 using oil may be arbitrary. Thus, for example, an oil introduction pipe inserted into the hollow portion 34A may be provided, or oil may be dripped from the radial outside toward the coil ends 29A, 29B through an oil passage that may be formed in the stator support portion 10.

[0029] Next, referring to FIG. 2 and subsequent figures, an example of a manufacturing apparatus 200 and a manufacturing method for the rotor 30 in the motor 1 of the above-mentioned embodiment will be described. In FIG. 2 and other figures, a Z direction parallel to the rotating shaft 12 is defined, as well as a Z1 side and a Z2 side along the Z direction. In the following, for the sake of explanation, as an example, the Z direction corresponds to the up-down direction during the manufacturing process, and the Z2 side is the lower side. In addition, in FIG. 2 and other figures, a reference axis I in the manufacturing apparatus 200 is shown. The reference axis I constitutes the central axis when centering the workpiece, and corresponds to the above-mentioned rotating shaft 12. In addition, in the following, terms such as an axial direction are based on the reference axis I. Therefore, for example, a radial direction corresponds to a radial direction of a rotating body centered on the reference axis I.

[0030] Fig. 2 is a cross-sectional view showing a schematic diagram of a manufacturing apparatus 200 for the rotor 30. Figs. 3 to 5 are explanatory diagrams of a pressure molding mechanism including a cam punch base 256, a cam driver 258, and a cam punch 260, Fig. 3 is an exploded perspective view of the pressure molding mechanism seen from below, Fig. 4 is a cross-sectional perspective view of the pressure molding mechanism cut along a plane passing through the reference axis I, and Fig. 5 is a perspective view of the pressure molding mechanism 25 seen from below in an assembled state. Note that in Fig. 3, some (two of four) of the cam punches 260 are omitted from illustration.

[0031] The manufacturing apparatus 200 includes a press machine 210 and a mold 240 .

[0032] The press machine 210 may have a normal configuration, and in this case, the manufacturing apparatus 200 can be formed by using an existing press machine. In the press machine 210, an upper slide 214 can slide (slide) in the vertical direction relative to a lower bolster (bed) 212. The position of the slide 214 in the vertical direction can be controlled. The bolster 212 is provided with a bed knockout pin 2122 that can move in the vertical direction. For example, the bed knockout pin 2122 has a function of lifting a workpiece from a lower die (a function of separating the workpiece from the lower die), and may be built into the bolster 212. The bed knockout pin 2122 may be the same as a bed knockout pin provided in a normal press machine. The bed knockout pin 2122 is capable of controlling the vertical position and / or load (the load in the vertical direction transmitted via the bed knockout pin 2122).

[0033] The mold 240 includes an upper mold 250 and a lower mold 270 .

[0034] The upper mold 250 includes an upper mold fixing portion 252 , a cam punch base 256 , a cam driver 258 , and a cam punch 260 .

[0035] The upper mold fixing part 252 is fixed to the slide 214 of the press machine 210. The upper mold fixing part 252 moves (rises and falls) integrally with the slide 214 in the up and down direction.

[0036] Cam punch base 256 is fixed to upper mold fixing portion 252. Therefore, cam punch base 256 moves (rises and falls) in the up and down direction integrally with upper mold fixing portion 252 and slide 214. Note that cam punch base 256 may be formed integrally with a part or all of upper mold fixing portion 252.

[0037] 3 to 5, the cam punch base 256 has a cylindrical shape that extends in the up-down direction, and has, on its lower end surface, a slide support portion 2562 that supports the cam driver 258. As shown in Figures 3 and 4, the slide support portion 2562 has a downward T-shaped cross-sectional shape when viewed in the radial direction, and extends in the radial direction with a uniform cross-section.

[0038] Also, as shown in FIG. 4, the cam punch base 256 has a slide hole 2564 formed by a hollow interior centered on the reference axis I, and the slide hole 2564 extends in the vertical direction with a uniform cross section (for example, a uniform rectangular cross section when viewed from above).

[0039] The cam driver 258 functions as a driving member that drives the cam punch 260. The cam driver 258 is supported by the cam punch base 256 in a manner such that the cam driver 258 is movable in the up and down direction relative to the cam punch base 256.

[0040] The cam driver 258 is movable in the vertical direction between an upper operative position and a lower inoperative position relative to the cam punch base 256. When the cam driver 258 moves between the operative position and the inoperative position, the cam punch 260 is displaced in conjunction therewith between a radially outer operative position and a radially inner inoperative position.

[0041] Cam driver 258 is pushed up to an upper operating position by driver drive pin 274, which will be described later. When cam driver 258 is axially separated from driver drive pin 274, which will be described later, it is located at a lower non-operating position due to the influence of gravity. Displacement of cam driver 258 relative to cam punch base 256, that is, displacement downward from the lower non-operating position, may be regulated by stopper 2581 (see FIG. 2, not shown in FIG. 4, etc.). The upper operating position may be fixed or variable, as will be described later.

[0042] The cam driver 258 includes a supported portion 2582 and a driving portion 2584 .

[0043] The supported portion 2582 is inserted into the slide hole 2564 of the cam punch base 256. The supported portion 2582 extends in the vertical direction with a uniform cross section (for example, a uniform rectangular cross section when viewed from above) corresponding to the slide hole 2564.

[0044] Driving portion 2584 extends in the up-down direction in a manner continuing from the lower end of supported portion 2582. Driving portion 2584 is disposed on the radially inner side of cam punch 260. Specifically, driving portion 2584 is disposed in hollow portion 262 (see FIG. 3) on the radially inner side of cam punch 260.

[0045] The cross-sectional area of ​​the driving portion 2584 (cross-sectional area when cut in a horizontal plane) increases toward the bottom. In the example shown in Fig. 3 to Fig. 5, the driving portion 2584 has a rectangular cross-sectional shape (e.g., a square cross-sectional shape). However, in a modified example, the driving portion 2584 may have another cross-sectional shape such as a polygonal shape depending on the division mode of the cam punch 260 (and the associated cross-sectional shape of the radially inner hollow portion 262) described later.

[0046] Driving unit 2584 has, on its outer circumferential surface (side surface), second inclined surfaces 25842 inclined with respect to the up-down direction. Second inclined surfaces 25842 are planar in shape and form the four side surfaces (outer circumferential surfaces) of driving unit 2584. The inclination angles (for example, inclination angles with respect to reference axis I; see the supplementary angle of angle θ in FIG. 12A described later) of second inclined surfaces 25842 on the four side surfaces of driving unit 2584 may be the same as each other.

[0047] The driving portion 2584 is disposed in the radially inner cavity 262 of the cam punch 260 in such a manner that the second inclined surface 25842 is in surface contact with a first inclined surface 2601 of the cam punch 260 described below. In this case, the surface contact between the driving portion 2584 and the cam punch 260 may be maintained even when the cam driver 258 is in any position between the upper operative position and the lower inoperative position.

[0048] Cam punch 260 is supported by slide support portion 2562 of cam punch base 256. Cam punch 260 is supported by cam punch base 256 in a manner such that cam punch 260 is displaceable in the radial direction relative to cam punch base 256.

[0049] The cam punch 260 is displaceable in the radial direction between a non-operating position on the radial inside and an operating position on the radial outside. When the cam punch 260 is in the non-operating position, it has a shape that allows it to be positioned within the hollow portion 34A of the rotor shaft 34. When the cam punch 260 is in the non-operating position on the radial inside, it has an outer shape (for example, an outer shape that is generally substantially circular or elliptical) that corresponds to the shape of the inner circumferential surface of the rotor shaft 34 when viewed from above. In this case, when the cam punch 260 is in the non-operating position on the radial inside, it may have an outer shape that is offset radially inward from the shape of the inner circumferential surface of the rotor shaft 34 when viewed from above.

[0050] Cam punch 260 is normally located at a non-operating position on the radially inner side. An elastic ring (not shown), which is a ring-shaped elastic member, may be provided in ring groove 261 of cam punch 260. In this manner, cam punch 260 may be biased toward the non-operating position on the radially inner side by biasing means such as an elastic ring (not shown).

[0051] The radial position of the cam punch 260 changes in conjunction with the axial displacement of the cam driver 258. Specifically, when the cam driver 258 moves from the lower non-operating position to the upper operating position, the cam punch 260 moves in conjunction with the movement from the radially inner non-operating position to the radially outer operating position. Also, when the cam driver 258 moves from the upper operating position to the lower non-operating position, the cam punch 260 moves in conjunction with the movement from the radially outer operating position to the radially inner non-operating position. When the cam punch 260 is in the radially outer operating position, it has an outer shape (for example, an overall substantially circular or elliptical outer shape) according to the shape of the inner peripheral surface of the rotor shaft 34 in a top view. In this case, when the cam punch 260 is in the radially outer operating position, it may have an outer shape (see the dashed line in FIG. 12B described later) that is offset radially outward from the shape of the inner peripheral surface of the rotor shaft 34 in a top view.

[0052] Cam punch 260 has a hollow portion 262 on the radially inner side. Hollow portion 262 continues from slide hole 2564 of cam punch base 256, and extends in the axial direction with reference axis I as its axis. Note that hollow portion 262 has a shape corresponding to drive portion 2584 of cam driver 258 in top view. Note that hollow portion 262 may have a cross-sectional shape that is rotationally symmetric with respect to reference axis I (a shape relating to a cross section when cut on a horizontal plane).

[0053] Cam punch 260 has a first inclined surface 2601 that is inclined in the up-down direction on an inner circumferential surface that forms hollow portion 262. First inclined surface 2601 forms a non-contact portion with which second inclined surface 25842 of drive portion 2584 of cam driver 258 comes into contact. First inclined surface 2601 has a function of converting a part of the force that cam punch 260 receives from drive portion 2584 into a radial force, as will be described later with reference to FIG. 12A.

[0054] Cam punch 260 has a function of applying a radial force to the inner peripheral surface of rotor shaft 34, thereby expanding the diameter of rotor shaft 34 in a manner involving plastic deformation. To be able to appropriately realize such a function, cam punch 260 is preferably configured to have high rigidity / hardness. For example, cam punch 260 may be formed from a metal material and be a substantially rigid body (a rigid body that does not substantially deform in the molding pressure step described below). When formed from a metal material, cam punch 260 is less susceptible to wear and the like compared to urethane, and can have significantly higher durability.

[0055] 3 to 5, as an example, cam punch 260 is divided into four in the circumferential direction, and each divided body forms cam slider 2602. In a modified example, cam punch 260 may be divided into five or more parts (see FIG. 15), or may be divided into three or less parts.

[0056] Each cam slider 2602 is supported by the slide support portion 2562 in such a manner that it can slide radially outward along the radial direction relative to the slide support portion 2562 of the cam punch base 256. In the example shown in Figs. 3 and 4, each cam slider 2602 has an engagement groove 2604 that engages with the slide support portion 2562, and the engagement groove 2604 has a downward T-shaped cross-sectional shape corresponding to the cross-sectional shape of the slide support portion 2562 when viewed in the radial direction, and extends in the radial direction with an equal cross section. Note that in the example shown in Figs. 3 to 5, each cam slider 2602 is a divided body divided into four, and therefore the respective sliding directions may be orthogonal to each other.

[0057] Each cam slider 2602 forms the above-mentioned first inclined surface 2601 in a one-to-one correspondence with each second inclined surface 25842 on the four side surfaces of the drive portion 2584. Moreover, the first inclined surface 2601 of each cam slider 2602 as a whole forms a radially outer boundary surface of the cavity portion 262. The inclination angle (for example, the inclination angle with respect to the reference axis I; see the supplementary angle of angle θ in FIG. 12A described later) of the first inclined surface 2601 of each cam slider 2602 may be the same as each other.

[0058] The lower die 270 includes a work support portion 272 and a driver drive pin 274 .

[0059] The work support portion 272 is a lower die fixing portion that is fixed to the bolster 212 of the press machine 210. The work support portion 272 supports the work including the rotor core 32 and the hollow rotor shaft 34 from below. At this time, the work support portion 272 creates a state in which the rotor shaft 34 is disposed on the inner diameter side of the rotor core 32 (see FIG. 8 described later).

[0060] The driver drive pin 274 functions as one component of the pressure molding mechanism. The driver drive pin 274 is movable in the vertical direction relative to the work support part 272 in a manner that allows it to abut against the lower end surface of the cam driver 258 (i.e., the lower end surface of the drive part 2584) in the vertical direction. The driver drive pin 274 may be movable in the vertical direction in a manner that allows it to be integral with the bed knockout pin 2122.

[0061] With its upper end surface in contact with the lower end surface of the cam driver 258, the driver drive pin 274 applies an axial force to the cam driver 258 based on the axial load from the bed knockout pin 2122. In other words, the driver drive pin 274 transmits the axial load from the bed knockout pin 2122 to the cam driver 258, thereby applying an axial force (upward force) to the cam driver 258.

[0062] According to such a manufacturing apparatus 200, the rotor 30 can be appropriately manufactured by the manufacturing method described below using an existing press machine 210. In a modified example, equipment may be used instead of the press machine 210. An example of the operation of the manufacturing apparatus 200 will be described in relation to the manufacturing method described below.

[0063] FIG. 6 is a schematic flow chart showing the flow of the present manufacturing method. FIGS. 7 to 11, 13, and 14 are cross-sectional views showing the state of the rotor shaft 34 and the rotor core 32 in the manufacturing apparatus 200 in several steps shown in FIG. 6. FIG. 12A is an enlarged view of part Q1 in FIG. 11, and is an explanatory diagram of the load transmission mode in the molding pressurizing step. FIG. 12B is an explanatory diagram showing the state of the cam punch 260 in the molding pressurizing step as viewed from above. FIG. 12B shows the cam punch 260 when it is in a non-operating position on the radial inside, and also shows a dashed line representing the outline of the cam punch 260 when it is in an operating position on the radial outside.

[0064] First, as shown in FIG. 7, this manufacturing method includes a preparation step (step S500) of preparing the rotor shaft 34 and the rotor core 32 (not joined to each other) as workpieces.

[0065] At this stage, rotor shaft 34 may have first step portion 346 and second step portion 347 described above. At this stage, rotor shaft 34 has an inner diameter r1' at a portion corresponding to expanded diameter portion 341 that forms the inner circumferential surface of first inner diameter r1 in the finished state, and inner diameter r1' may be slightly smaller than first inner diameter r1 (see FIG. 1) in the finished state. At this stage, rotor shaft 34 may have outer diameter r20 that is the same as inner diameter r10 of rotor core 32 or slightly smaller than inner diameter r10.

[0066] Similarly to the rotor shaft 34, the rotor core 32 at this stage may have an outer diameter slightly smaller than that of the finished product. This is because the rotor core 32 deforms slightly radially outward as the rotor shaft 34 expands in a fastening process described later.

[0067] Next, as shown in Fig. 8, this manufacturing method includes a step (step S501) (an example of an arrangement step) of setting the rotor shaft 34 and the rotor core 32 in the manufacturing apparatus 200. At this time, the work support portion 272 of the lower mold 270 of the manufacturing apparatus 200 simultaneously supports the rotor shaft 34 and the rotor core 32 from below, and restricts downward movement (displacement) of the rotor shaft 34 and the rotor core 32. Fig. 8 shows a schematic state at the end of step S501.

[0068] It is not necessary that the rotor shaft 34 and the rotor core 32 are set on the workpiece support portion 272 of the manufacturing apparatus 200 at the same time, and they may be set on the workpiece support portion 272 of the manufacturing apparatus 200 in order.

[0069] Next, the manufacturing method includes a process of starting the descent of upper mold 250 (step S502) and lowering upper mold 250 to the preparation position (step S504). Fig. 9 shows a schematic diagram of the state at the end of step S504.

[0070] Next, the manufacturing method includes an integration step (step S506) of integrating the rotor core 32 and the rotor shaft by expanding the diameter of the rotor shaft.

[0071] In this embodiment, the integration process is performed for each of the multiple axially formed target regions on the inner peripheral surface of the rotor shaft 34. In this case, the integration process may be performed in order from the top of the multiple axially formed target regions. Hereinafter, the region among the multiple axially formed target regions that is to be formed and pressed in the current integration process is referred to as the "current formed target region."

[0072] The integration process (step S506) first includes a molding positioning process (step S5061) (an example of a positioning process) in which upper die 250 is further lowered and cam punch 260 is positioned relative to rotor shaft 34 so that cam punch 260 radially faces or contacts the current molding target region on the inner peripheral surface of rotor shaft 34. Fig. 10 shows a schematic state at the end of step S5061 when the first molding target region from the top among multiple molding target regions in the axial direction is the current molding target region.

[0073] 10, in parallel with the molding positioning step (step S5061), the bed knockout pin 2122 is raised to a position immediately before the driver drive pin 274 abuts against the cam driver 258. However, in a modified example, such raising of the bed knockout pin 2122 may be performed after the molding positioning step (step S5061) and before step S5062, or may be performed before the molding positioning step (step S5061).

[0074] The integration process (step S506) then includes a molding pressurizing process (step S5062) (an example of a load applying process) in which the cam punch 260 is displaced (slid) in the radial direction by transmitting an axial load from the bed knockout pin 2122 to the cam driver 258 via the driver drive pin 274. FIG. 11 shows a schematic diagram of the state during the molding pressurizing process (step S5062).

[0075] In the molding pressurization step (step S5062), the driver drive pin 274 pushes up the cam driver 258 based on the axial load from the bed knockout pin 2122. When the cam driver 258 is pushed up, as shown in FIG 12A, the cam punch 260 is pushed outward in the radial direction toward the radially outer operating position with the second inclined surface 25842 of the cam driver 258 and the first inclined surface 2601 of the cam punch 260 in contact with each other.

[0076] In the process of displacing the cam punch 260 to the radially outer operating position, the cam punch 260 abuts against the current forming target area on the inner peripheral surface of the rotor shaft 34 in the radial direction. Then, when the cam punch 260 is further displaced to the radially outer operating position, a force F3 perpendicular to the abutment surface between the second inclined surface 25842 of the cam driver 258 and the first inclined surface 2601 of the cam punch 260 is generated in response to a reaction force (a reaction force directed radially inward) from the rotor shaft 34. As shown in FIG. 12A, this force F3 is divided into an up-down component F1 and a radial component F2 directed radially outward, and the magnitude of the force F3 depends on the magnitude of the axial load from the bed knockout pin 2122. The magnitude of the radial component F2 can be expressed as F2=F3×sinθ. In this case, the angle θ corresponds to the inclination angle of the first inclined surface 2601 (and the second inclined surface 25842) with respect to the horizontal plane, as shown in FIG. 12A.

[0077] Then, by further increasing the axial load from the bed knockout pin 2122 (i.e., by increasing the radial component F2), the cam punch 260 is further displaced to the radially outer operating position, and the cam punch 260 reaches the operating position in a manner accompanied by plastic deformation of the rotor shaft 34. That is, the increased radial component F2 acts radially outward on the current forming target area (see area P in FIG. 12A) on the inner peripheral surface of the rotor shaft 34, and the rotor shaft 34 expands in diameter accompanied by plastic deformation. In this way, when the driver drive pin 274 is pushed up to the operating position and the cam punch 260 reaches the operating position, the rotor shaft 34 expands in diameter accompanied by plastic deformation. As a result, the rotor shaft 34 expands in diameter in the axial range corresponding to the current forming target area, and integration between the rotor core 32 and the rotor shaft 34 is realized.

[0078] Here, the radial interference between the rotor core 32 and the rotor shaft 34 realized in the molding pressurization step (step S5062) is determined according to the radial displacement (slide amount) Δd (see FIG. 12B) of the cam punch 260 from when the cam punch 260 abuts against the inner peripheral surface of the rotor shaft 34 to when it reaches the operating position. This radial displacement (slide amount) Δd of the cam punch 260 is determined by the difference between the vertical position of the driver drive pin 274 when the cam punch 260 abuts against the inner peripheral surface of the rotor shaft 34 and the vertical position of the driver drive pin 274 when it reaches the operating position. The vertical movement amount related to such a difference can be precisely controlled through the vertical position control of the bed knockout pin 2122. In this way, according to this embodiment, the radial interference between the rotor core 32 and the rotor shaft 34 can be precisely controlled through the position control of the bed knockout pin 2122.

[0079] The integration step (step S506) then includes a pressure release step (step S5063) in which the bed knockout pin 2122 and the driver drive pin 274 are slightly lowered to return the cam driver 258 to the inoperative position. Accordingly, the cam punch 260 is returned radially inward from the operative position to the inoperative position. Note that a ring-shaped elastic body (not shown) may be wound around the ring groove 261 (see FIG. 4) of the cam punch 260 as a return mechanism for realizing such radial movement of the cam punch 260. In this case, the elastic ring can simultaneously bias the four cam sliders 2602 radially inward toward the inoperative position.

[0080] In this embodiment, the driving unit 2584 of the cam driver 258 located in the cavity 262 radially inside the cam punch 260 can apply a radial force (see radial component F2) to the cam punch 260. At this time, the forming target area (see area P in FIG. 12A) on the inner peripheral surface of the rotor shaft 34 overlaps with the contact area between the cam punch 260 and the cam driver 258 (i.e., the contact area between the first inclined surface 2601 and the second inclined surface 25842) when viewed in the radial direction. This makes it possible to uniformize the radial force applied to the inner peripheral surface of the rotor shaft 34 via the cam punch 260 over the entire axial range of the forming target area. In this way, according to this embodiment, it is possible to appropriately control the tightening between the rotor core 32 and the rotor shaft 34 over the entire axial range of the forming target area, thereby controlling the desired tightening.

[0081] In this embodiment, the integration step (step S506) is repeatedly performed for each molding and pressurizing region divided in the axial direction (step S507). For example, when the integration step (step S506) for the first molding and pressurizing region from the top as shown in Fig. 11 is completed, the next integration step (step S506) is performed for the second molding and pressurizing region from the top. Specifically, as shown in Fig. 13, a molding positioning step (step S5061) is performed for the second molding and pressurizing region from the top, and then, as shown in Fig. 14, a molding and pressurizing step (step S5062) is performed for the second molding and pressurizing region from the top.

[0082] In this embodiment, the inner peripheral surface of the rotor shaft 34 is divided into a plurality of molding and pressurizing regions in the axial direction, and the integration process (step S506) is performed for each molding and pressurizing region. This makes it possible to appropriately control the interference over the axial range of the fitting region to a desired value, even if the axial range of the fitting region between the rotor shaft 34 and the rotor core 32 is relatively long.

[0083] Incidentally, even with the same internal pressure, the amount of radially outward deformation of the rotor shaft 34 may differ depending on the axial position of the rotor shaft 34. This is because the rigidity of the rotor shaft 34 may differ at each axial position due to differences in the cross-sectional shape of the rotor shaft 34, etc. For example, under the same internal pressure condition, the amount of radially outward deformation of the rotor shaft 34 is likely to be larger at the center side of the axial range of the fitting region between the rotor shaft 34 and the rotor core 32 than at the end of the axial range on the second step portion 347 side. For this reason, when the same internal pressure is applied over the entire axial range of the fitting region, it is difficult to make the interference uniform over the axial range of the fitting region.

[0084] In this respect, in this embodiment, the inner peripheral surface of the rotor shaft 34 is divided into a plurality of molding pressure regions in the axial direction, and the integration step (step S506) is performed for each molding pressure region, so that the force F3 (see FIG. 12A) applied from the cam driver 258 to the cam punch 260 via the driver drive pin 274 can be changed for each molding pressure region. This makes it possible to change the radial component F2 (see FIG. 12A) applied to the molding pressure region via the cam punch 260 for each molding pressure region. Therefore, according to this embodiment, it is possible to precisely control (adjust) the tightening margin over the axial range of the fitting region. Therefore, according to this embodiment, it is possible to uniformize the tightening margin over the entire axial range of the fitting region for each molding pressure region. On the other hand, according to this embodiment, it is also possible to make the tightening margin larger in a part of the axial range of the fitting region than in the other parts, as necessary.

[0085] Furthermore, in this embodiment, since the integration step (step S506) is executed for each molding pressure region, it is also possible to change the upper operating position of cam driver 258 (and accordingly the radially outer operating position of cam punch 260) for each molding pressure region. For example, the upper operating position of cam driver 258 for one molding pressure region may be set higher than the upper operating position of cam driver 258 for another molding pressure region. In this case, the radially outer operating position of cam punch 260 for one molding pressure region is located radially outer than the radially outer operating position of cam punch 260 for another molding pressure region, so that it is possible to increase the clamping margin accordingly.

[0086] In this embodiment, the multiple molding and pressurizing regions in which the integration step (step S506) is performed individually as described above may be set in a manner that they overlap with each other in the axial direction. For example, a part of the axial upper side of the first molding and pressurizing region from the top may overlap with a part of the axial upper side of the first molding and pressurizing region from the top. The multiple molding and pressurizing regions are set to cover a part of the axial direction on the inner peripheral surface of the rotor shaft 34, and a part of the range corresponding to the fitting region between the rotor shaft 34 and the rotor core 32 (i.e., a range overlapping with the rotor core 32 when viewed in the radial direction), without omission, but may also be set to a range exceeding the part of the range. For example, in the example shown in FIG. 11 and FIG. 12A, the first molding and pressurizing region from the top overlaps only a part of the lower side with the fitting region between the rotor shaft 34 and the rotor core 32 when viewed in the radial direction. However, the upper boundary of the first molding and pressurizing region from the top may be aligned with the fitting region between the rotor shaft 34 and the rotor core 32.

[0087] Incidentally, there is known a technique for ensuring the interference between the rotor shaft 34 and the rotor core 32 by introducing a urethane member into the hollow portion 34A of the rotor shaft 34 and expanding the urethane member to expand the diameter of the rotor shaft 34. With such a technique, wear of the urethane member (and the associated shortened lifespan) can easily become a problem.

[0088] In this regard, according to this embodiment, the cam punch 260 can be made of a material (such as a metal material) that is highly wear-resistant, unlike urethane, and therefore problems that may arise when using a member made of urethane can be avoided.

[0089] Also, a technique (hydroforming) is known in which a high-pressure fluid is introduced into the hollow portion 34A of the rotor shaft 34 to expand the diameter of the rotor shaft 34, thereby ensuring the interference between the rotor shaft 34 and the rotor core 32. However, such a technique has a problem in that the seal structure for sealing the high-pressure fluid in the hollow portion 34A of the rotor shaft 34 becomes complicated.

[0090] In this regard, according to the present embodiment, the tightening clearance between the rotor shaft 34 and the rotor core 32 can be secured without using high-pressure fluid, thereby avoiding problems that may arise when using high-pressure fluid (e.g., complicated sealing structure).

[0091] Returning to FIG. 6, when the integration step (step S506) is completed, this manufacturing method includes a step of raising upper die 250 to the top dead center (step S508).

[0092] Next, the manufacturing method includes a jet hole forming step (step S509) for forming holes corresponding to the oil holes 348, 349 in the rotor shaft 34. The jet hole forming step may be performed by machining or the like after the rotor shaft 34 is removed from the manufacturing apparatus 200. When the jet hole forming step (step S508) is completed, the final rotor shaft 34 is completed.

[0093] Next, this manufacturing method includes a finishing process (step S510) that may include a process of fixing the permanent magnet 321, a process of magnetizing the magnet, a process of adjusting the rotation balance by the end plates 35A and 35B, and the like.

[0094] In this manner, according to the present manufacturing method, the rotor core 32 and the rotor shaft 34 can be integrated together by the manufacturing apparatus 200 including the die 240 fixed to the press machine 210. Furthermore, according to the present manufacturing method, it is possible to ensure a desired interference over the entire axial range of the fitting region between the rotor shaft 34 and the rotor core 32.

[0095] Next, various modifications of the above-mentioned embodiment will be described with reference to FIG. 15 and subsequent figures.

[0096] FIG. 15 is an explanatory diagram of a modification of cam punch 260 according to the embodiment described above, showing only the outer shape of cam punch 260A according to this modification as viewed from above.

[0097] The cam punch 260A according to this modification is divided into eight parts in the circumferential direction, and each part forms a cam slider 2602A.

[0098] The cam punch 260A has a larger number of circumferential divisions than the cam punch 260 according to the embodiment described above, and accordingly the circumferential range covered by one cam slider 2602A in the molding pressure region is narrower. Therefore, the greater the number of circumferential divisions, the more uniform the tightening margin between the rotor shaft 34 and the rotor core 32 can be over the entire circumferential range of the region to be molded. However, the greater the number of circumferential divisions, the greater the disadvantage in terms of strength, and the number of divisions may be adjusted taking such a trade-off into consideration.

[0099] Alternatively, the cam punch 260 according to the embodiment described above may be rotatable about the reference axis I. In this case, as shown in Fig. 12B and Fig. 16, by performing the integration step (step S506) while rotating the cam punch 260 about the reference axis I for the same molding pressure region, an effect similar to that of the modified example shown in Fig. 15 can be obtained. In other words, it is possible to uniform the interference between the rotor shaft 34 and the rotor core 32 over the entire circumferential range of the region to be molded.

[0100] In this case, cam punch 260 may be configured to be rotatable about reference axis I by cam punch base 256 being configured to be rotatable about reference axis I. Cam punch base 256 may be rotatably supported by upper die fixing portion 252 via a rotating table such as an index table.

[0101] In addition, the configuration in which cam punch 260 is rotatable around reference axis I and the integration process (step S506) is performed while rotating cam punch 260 around reference axis I for the same molding pressure region is suitable when the shape of the inner surface of rotor shaft 34 (shape when viewed from above) is circular.

[0102] FIG. 17 is a perspective view for explaining a pressure molding mechanism 17 which can be substituted for the cam punch 260 and the like according to the above-mentioned embodiment.

[0103] The pressure molding mechanism 17 according to this modified example is a mechanism that utilizes a collet punch, and includes a collet 170 as an operating member, a first driving member 171, and a second driving member 172.

[0104] The collet 170 is an operating member that performs the same function as the cam punch 260 according to the above-mentioned embodiment, and is elastically deformable in the radial direction. The collet 170 is cylindrical with a cavity 1708 formed on the inner periphery. The collet 170 may have slits 1701, 1702 along the up-down direction alternately at equal intervals in the circumferential direction so as to facilitate elastic deformation in the radial direction. In this case, the slit 1701 extends from the upper end to halfway down, and the slit 1702 extends from the lower end to halfway up.

[0105] Collet 170 has a tapered surface 1704 on the lower end side of its inner circumferential surface, and a tapered surface (not visible in FIG. 17) on the upper end side of its inner circumferential surface. Tapered surface 1704 on the lower end side is formed over the entire circumferential direction while being inclined with respect to reference axis I. Tapered surface 1704 is formed in a manner that becomes thinner toward the upper side (in the case where the cross section is circular, the inner diameter becomes smaller). In addition, the tapered surface on the upper end side may be vertically symmetrical to tapered surface 1704.

[0106] The first driving member 171 may be fixed to the upper die fixing portion 252 instead of the cam punch base 256 according to the embodiment described above. The first driving member 171 extends in the vertical direction centered on the reference axis I, and has a tapered surface (inclined surface) 1710 on the lower end side. The tapered surface 1710 of the first driving member 171 contacts the upper tapered surface (not visible in FIG. 17) which is the contacted portion of the collet 170 in the hollow portion 1708 of the collet 170. At this time, the tapered surface 1710 comes into surface contact with the upper tapered surface (not visible in FIG. 17) of the collet 170.

[0107] The second driving member 172 may be movable in the vertical direction in a manner integral with the bed knockout pin 2122, instead of the driver driving pin 274 according to the above-mentioned embodiment. The second driving member 172 extends in the vertical direction centered on the reference axis I, and has a tapered surface (inclined surface) 1720 on the lower end side. The tapered surface 1720 of the second driving member 172 contacts the lower tapered surface 1704, which is the contacted portion of the collet 170, in the hollow portion 1708 of the collet 170. At this time, the tapered surface 1720 is in surface contact with the lower tapered surface 1704 of the collet 170. The second driving member 172 may support the collet 170 during the molding pressurization step. In this case, the outer diameter of the tapered surface 1720 may be set to be larger than the outer diameter of the collet 170 at the maximum possible deformation.

[0108] The pressure molding mechanism 17 according to this modification can also realize the molding pressurization process by the cam punch 260 and the like according to the above-mentioned embodiment. That is, when the first driving member 171 is lowered, the tapered surface 1710 of the first driving member 171 contacts the upper tapered surface (not visible in FIG. 17) of the collet 170 in the hollow portion 1708 of the collet 170. Then, when the first driving member 171 is further lowered to the operating position in a state in which the collet 170 faces the molding pressurization area on the inner peripheral surface of the rotor shaft 34 in the radial direction, the upper side of the collet 170 deforms radially outward to the operating position on the radially outer side, and the rotor shaft 34 expands in diameter with plastic deformation. Similarly, the tapered surface 1720 of the second driving member 172 contacts the lower tapered surface 1704 of the collet 170 in the hollow portion 1708 of the collet 170. Then, when the collet 170 is radially opposed to the molding pressure region on the inner surface of the rotor shaft 34 and the second driving member 172 is further raised to the operating position, the lower side of the collet 170 deforms radially outward to the radially outer operating position, and the rotor shaft 34 expands in diameter due to plastic deformation.

[0109] In the case of the pressure molding mechanism 17 according to this modification, the integration process (see step S506 in FIG. 6) may be repeatedly performed for each of the molding and pressurizing regions divided in the axial direction. This makes it possible to appropriately control the interference over the axial range of the fitting region to a desired value, even if the axial range of the fitting region between the rotor shaft 34 and the rotor core 32 is relatively long.

[0110] Although each embodiment has been described in detail above, it is not limited to a specific embodiment, and various modifications and changes are possible within the scope of the claims. It is also possible to combine all or a plurality of the components of the above-mentioned embodiments. Furthermore, among the effects of each embodiment, the effects related to the dependent claims are additional effects that are distinguished from the generic concept (independent claim).

[0111] For example, in the embodiment described above, in the integration step (see step S506 in FIG. 6), the cam punch 260 etc. is positioned with respect to each molding pressure region of the work by raising and lowering the upper die 250 etc. while the work is fixed, but the work side may be moved. Also, in the embodiment described above, the bed knockout pin 2122 is used to apply an axial load for expanding the diameter of the rotor shaft 34, but a similar axial load may be applied from the upper die 250 side.

[0112] In addition, in the above-described embodiment, the integration step (see step S506 in FIG. 6) is performed once for each molding and pressure application region, but it may be performed two or more times for some or all of the molding and pressure application regions. [Explanation of symbols]

[0113] 1···motor, 30··rotor, 32··rotor core, 34··rotor shaft, 200··manufacturing device, 210··press machine, 214··slide, 212··bolster, 2122···bed knockout pin (load application portion), 250··upper die, 252···upper die fixing portion (positioning means), 256···cam punch base (positioning means, base member), 258···cam driver (driving member), 25842···second inclined surface, 260···cam punch (operating member), 262·· ·Hollow portion, 2602, 2602A···cam slider (divided body), 2601···first inclined surface (contacted portion), 270···lower die, 272···workpiece support portion (lower die fixing portion), 170···collet (operating member), 1704···tapered surface (first inclined surface), 1708···hollow portion, 171···first driving member (driving member), 1710···tapered surface (second inclined surface), 172···second driving member (driving member), 1720···tapered surface (second inclined surface), P···area (molding pressure area), I···reference axis (axis)

Claims

1. A method for manufacturing a rotor for a rotating electric machine, comprising the steps of: an arrangement step of supporting a workpiece including a rotor core and a hollow rotor shaft and forming a state in which the rotor shaft is arranged on an inner diameter side of the rotor core; a positioning step of positioning an actuating member that can be disposed in a hollow interior of the rotor shaft, has a cavity on the radially inner side, and is radially displaceable or deformable, relative to the rotor shaft so that the actuating member faces or comes into contact with a molding pressure region on an inner circumferential surface of the rotor shaft in the radial direction; a load application process, which applies an axial force to a driving member after the placing process and the positioning process, thereby bringing the driving member into contact with a contacted portion of the operating member within the hollow portion of the operating member while applying a radial force to the operating member.

2. The manufacturing method according to claim 1 , wherein the positioning process is performed multiple times for one of the workpieces so that the operating member faces or contacts radially each of a plurality of axial molding pressure regions on the inner surface of the rotor shaft.

3. 3. The manufacturing method according to claim 2, wherein the load application process is performed for each of the positioning processes for one of the workpieces, and a force of a different magnitude is applied to the driving member when the load application process is performed corresponding to one of the positioning processes and when the load application process is performed corresponding to another of the positioning processes.

4. A manufacturing apparatus for a rotor for a rotating electric machine, comprising: a work support portion that supports a workpiece including a rotor core and a hollow rotor shaft and creates a state in which the rotor shaft is disposed on an inner diameter side of the rotor core; an actuating member disposable within the hollow interior of the rotor shaft, the actuating member having a cavity on a radially inner side and capable of being displaced or deformed in a radial direction; a drive member that contacts a contacted portion of the actuating member within the cavity of the actuating member; a positioning means for positioning the operating member with respect to the rotor shaft so that the operating member faces or comes into contact with a molding pressure region on an inner peripheral surface of the rotor shaft in a radial direction; a load applying unit that applies an axial force to the driving member located within the hollow portion of the operating member positioned by the positioning means, thereby applying a radial force to the operating member while bringing the driving member into contact with the contacted portion.

5. The manufacturing apparatus according to claim 4 , wherein the contacted portion faces the molding pressure region in a radial direction.

6. The positioning means includes a base member that is vertically movable with respect to the workpiece, the actuating member is slidable in a radial direction relative to the base member, and has a first inclined surface inclined with respect to an axial direction at the contacted portion; The manufacturing apparatus according to claim 4 or 5, wherein the driving member has a second inclined surface that is in surface contact with the first inclined surface.

7. The manufacturing apparatus according to claim 6 , wherein the operating member is divided in a circumferential direction, and each divided part forms the first inclined surface.

8. The manufacturing apparatus according to claim 7 , wherein the base member is rotatable about an axis relative to the workpiece.

9. The manufacturing apparatus according to any one of claims 4 to 8, wherein the positioning means positions the actuating member relative to the rotor shaft so that the actuating member faces or contacts the rotor shaft radially in each of a plurality of axial molding pressure regions on the inner peripheral surface of the rotor shaft.

10. The manufacturing apparatus according to any one of claims 4 to 9, wherein the load applying section applies a force of different magnitude to the driving member when the operating member radially faces or contacts a first molding and pressure region among the plurality of molding and pressure regions and when the operating member radially faces or contacts a second molding and pressure region different from the first molding and pressure region.

11. The manufacturing apparatus according to claim 4 , wherein the operating member and the driving member form a cam mechanism and are each made of a metallic material.

12. A press machine having a slide and a bolster that can be raised and lowered in the vertical direction; an upper mold including an upper mold fixing portion fixed to the slide; a lower die including the work support portion fixed to the bolster and facing the upper die in the up-down direction, The positioning means includes the upper mold fixing portion, The operating member is supported by the upper die fixing portion, The drive member is supported by the upper mold fixing portion, The manufacturing apparatus according to claim 4 , wherein the load applying portion includes a bed knockout pin provided on the bolster.

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