JPH1066287A - Magnet generator rotor - Google Patents

Abstract

(57) [Summary] (with correction) [PROBLEMS] To reduce the cost of the rotor 1 by joining a boss 2 and an iron bowl 4. The joint between the boss 2 and the iron bowl 4 is not damaged by the radial stress. SOLUTION: A large number of knurls are formed on an outer peripheral portion 2c of a boss 2, and by driving an inner peripheral portion 4c of an iron bowl 4,
A coupling in the direction of rotation is made. On one side of the outer peripheral portion 2c,
An iron bowl receiving portion 2e for receiving the iron bowl 4 is provided. A caulking 2f for caulking the driven iron bowl 4 is provided on the other side of the outer peripheral portion 2c. Further, the position of the joining portion for joining the boss 2 and the iron bowl 4 is provided at a position where the radial stress is minimum. Thus, the rotor 1
The joint between the boss 2 and the iron bowl 4 and the axial connection by caulking make it possible to keep the cost of the rotor 1 very low. Also, since the joint position has the minimum radial stress, even if the joint is caulked,
Sufficient axial strength can be obtained.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a technique for joining a boss and an iron bowl in a rotor of a magnet generator, and more particularly to a technique for fixing the boss and the iron bowl in an axial direction.

[0002]

2. Description of the Related Art The rotor of a magnet generator mounted on a motorcycle or the like has an integral molding technique in which a boss fixed to a rotary drive shaft and an iron bowl holding a magnet are integrally formed by forging and finished by cutting. Separate joining technology that joins a boss finished by cutting after forging and an iron bowl of a press-formed product by welding or metal flow that makes the iron bowl concave and flows the iron bowl material into the groove provided in the boss And is known.

[0003] The rotor formed by the integral molding technique has a large machining allowance and a high processing cost, and as a result, there is a problem that the cost of the rotor increases. Similarly, in the case of welding, there arises a problem that the cost due to special equipment for welding increases. On the other hand, a rotor with separate joining technology using metal flow can greatly reduce the cutting allowance and cost compared to the one-piece molding technology, but if you try to reduce the moment of inertia of the rotor by making the iron bowl thinner In addition, since the iron bowl is depressed, the margin for joining the boss and the iron bowl is reduced, and there is a problem that the required bonding strength cannot be secured.

The mechanism of breakage due to insufficient bonding strength will be specifically described. When the rotor rotates at a high speed such as 10000 rpm, the outer peripheral side of the iron bowl vibrates in the axial direction due to dynamic imbalance and centrifugal force of the rotor. Also, the eccentric rotation of the drive shaft causes the outer peripheral side of the iron bowl to vibrate in the axial direction.
Further, the outer peripheral side of the iron bowl also vibrates in the axial direction due to the axial displacement generated when the drive shaft rotates. When the rotor rotates at a high speed in this manner, an axial vibration is generated on the iron bowl side, so that a tensile stress (radial stress) is generated in a welded portion between the boss and the iron bowl. For this reason, if the joint between the boss and the iron bowl has insufficient bonding strength, the weld is likely to be damaged.

A technique disclosed in Japanese Patent Application Laid-Open No. 60-59953 is known as a technique for simultaneously solving the problem caused by the integral molding technique and the problem caused by the separate joining technique. This technology reduces the cost of the rotor by adopting the separate joining technology, and focuses on the fact that when the rotor rotates at high speed, the outer axial vibration and the inner vibration are in opposite phases. Then, a portion where the radial stress applied to the weld is small is found, and the weld is provided at the portion where the radial stress is small, thereby avoiding breakage of the weld.

[0006]

The technique disclosed in the above-mentioned publication can reduce the cost of the rotor and avoid damage to the welded portion. Therefore, it is necessary to use a special and expensive welding device. For this reason, there is a demand to further reduce the cost of the rotor by joining the boss and the iron bowl using an inexpensive joining device.

[0007]

SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and has a rotor provided by joining a boss and an iron bowl, so that the cost of the rotor can be suppressed, and the boss and iron caused by radial stress can be reduced. An object of the present invention is to reduce the cost of the rotor by joining the boss and the iron bowl using an inexpensive joining device, which can avoid damage to the joint part with the bowl.

[0008]

Means for Solving the Problems To achieve the above object, the rotor of the magnet generator according to the present invention employs the following technical means. [Means of Claim 1] By adopting claim 1 and manufacturing a rotor by joining a boss and an iron bowl, an inexpensive pressed product can be used for the iron bowl. For this reason, compared with the technique of forming the boss and the iron bowl integrally by forging and finishing by cutting, the cutting allowance is greatly reduced, and the cost of the rotor can be reduced.

The boss is pressed into the iron bowl, the iron bowl hits the iron bowl receiving portion of the boss, and the caulking portion of the boss crimps the iron bowl. Are fixed in the axial direction. That is, the boss and the iron bowl can be fixed in the axial direction by caulking the crimped portion of the boss to the iron bowl using a press machine that is less expensive than a welding device. As described above, since the boss and the iron bowl are joined by a less expensive press working machine as compared with the related art, the cost of the rotor can be further reduced.

Further, according to the first aspect, the joint between the outer peripheral portion of the boss and the inner peripheral portion of the iron bowl is provided at a position where the stress in the radial direction is substantially minimum. As a result, even if the rotor rotates at high speed and an axial vibration is generated on the iron bowl side, almost no radial stress is applied to the joint between the boss and the iron bowl. Therefore, even if the structure in which the boss and the iron bowl are joined in the axial direction by the pressure contact force and crimping of the boss and the iron arm as described above is used, there is no reduction in the pressure contact force of the joint portion, and the joint is damaged by the axial vibration load. Can be avoided.

[Claim 2] The outer diameter of the caulked portion is
A point on the inner side of the iron bowl where the outer periphery of the boss and the inner periphery of the iron bowl start to contact on the side of the caulking part is provided on the inner side of the iron bowl. Is provided on one side (iron bowl receiving part side) of a predetermined dimension from the side that is crimped with the boss, so that there is a gap between the crimping part side of the outer peripheral part of the boss and the crimping part side of the inner peripheral part of the iron bowl. Will occur. That is, since the outer peripheral portion of the boss and the inner peripheral portion of the iron bowl are not connected at the caulking portion side, when an axial force is applied to the iron bowl, the iron bowl is likely to vibrate in the axial direction. Therefore,
By providing a protruding portion that protrudes toward the inner peripheral side of the iron bowl on the caulking portion side of the inner peripheral portion of the iron bowl, and providing the protruding portion so as to contact the outer peripheral surface at the base of the caulking portion, the outer peripheral portion of the boss And the inner periphery of the iron bowl are also connected at the caulking part side, so that even if an axial force is applied to the iron bowl, the iron bowl can be prevented from vibrating in the axial direction, and the vibration resistance of the iron bowl Performance can be improved.

According to a third aspect of the present invention, in a case where a clutch outer for a starter clutch is provided on a rotor in addition to a boss and an iron bowl, in the prior art which does not employ the third aspect, the clutch outer is fixed by a fastener such as a bolt. It was fixed only to the boss. If the existing clutch outer is used as it is, the position of the fastener for fixing the clutch outer may interfere with the minimum position of the radial stress. is there. In that case, the third aspect is adopted, a joint is provided on the inner side of the fastener slightly to fix the clutch outer, and the iron bowl receiving portion of the boss is sandwiched between the iron bowl and the clutch outer. , The iron bowl and the clutch outer are fastened together by fasteners.

[0013] In order to avoid such interference, the position of the joint portion is provided slightly inward from the minimum position of the radial stress, so that the radial stress applied to the joint portion is slightly increased from the minimum position and the clutch is provided. The outer itself acts as a weight and acts to apply radial stress to the joint, but by adopting a structure in which the iron bowl receiving part is sandwiched between the boss and the clutch outer and fastened together, the iron bowl receiving part However, it is surely subjected to radial stress. For this reason, the radial stress at the joint is reduced, and it is possible to avoid a problem that the joint is damaged by the radial stress.

According to a fifth aspect of the present invention, a plurality of groove-shaped knurls are provided on the outer periphery of the boss, and the inner periphery of the iron bowl is pressed into the outer periphery of the boss. The applied rotational force can be reliably transmitted to the iron bowl via the joint, and the problem that the joint is damaged by the rotational stress applied to the boss and the iron bowl can be avoided.

According to the eighth aspect of the present invention, the cylindrical caulking portion before being caulked to the iron bowl is provided in a tapered shape which becomes thinner toward the front end. Since it is easy to be deformed in the radial direction, the cylindrical caulked portion can be easily curled toward the outside, and the productivity is excellent.

According to the ninth aspect of the present invention, when the caulking portion having a tubular shape before being caulked to the iron bowl is caulked to the iron bowl, the outer peripheral side is crushed to the iron bowl side by caulking. Since the caulking portion caulks the iron bowl, the shape of the caulking portion can be simplified, and the joining strength in the axial direction of the joining portion increases.

According to a tenth aspect of the present invention, a corner groove between the outer peripheral portion of the boss and the iron bowl receiving portion is formed with a relief groove that is recessed in the inner diameter direction, thereby forming a corner portion of the iron bowl. Thus, the problem of interference with the corner can be avoided.

[Embodiment 11] By adopting the eleventh aspect, a relief groove which is recessed in the axial direction is formed in a corner portion between the outer peripheral portion of the boss and the iron bowl receiving portion. When,
The problem of interference with the corner can be avoided. Further, the width at which the outer peripheral portion of the boss and the inner peripheral portion of the iron bowl are in contact with each other is increased, and the bonding strength can be improved.

According to a twelfth aspect of the present invention, a common relief groove recessed in both the inner diameter direction and the axial direction is formed in the corner portion between the outer peripheral portion of the boss and the iron bowl receiving portion. By doing so, it is possible to avoid the problem that the corners of the iron bowl and the corners interfere with each other, and by pressing the cutting tool against the corners of the rotating boss, a relief groove can be easily formed,
The productivity of the relief groove is improved.

[0020]

Next, an embodiment of the present invention will be described with reference to first to seventh embodiments. [First Embodiment] A first embodiment will be described with reference to FIGS. FIG. 1 is a sectional view of a rotor of a magnet generator.

The magnet generator is mounted on an end of a motorcycle engine. A rotor 1 used in the magnet generator is fixed to an end of a crankshaft (corresponding to a rotary drive shaft, not shown). A boss 2 which is driven to rotate,
The boss 2 is provided concentrically with the outer periphery of the boss 2, and is provided on the inner peripheral surface thereof by joining an iron bowl 4 to which the permanent magnet 3 is fixed.

Next, the boss 2, the iron bowl 4, and the joining of the boss 2 and the iron bowl 4 of the rotor 1 will be sequentially described. The boss 2 is formed by forging a steel material and then by machining such as cutting. The boss 2 extends at right angles to the tapered portion 2a fixed to the end of the crankshaft in the outer diameter direction, and has a circular plate. It has a flange portion 2b provided in a shape. The shape and the like of the outer peripheral end of the collar portion 2b will be described later.

The iron bowl 4 is made by rolling a rolled steel plate into an annular bowl shape by press working, and has a disk-shaped flat portion 4 a joined to the flange portion 2 b of the boss 2. The shape and the like of the inner peripheral end of the flat portion 4a will be described later. Inside the iron bowl 4, a ferrite or rare earth permanent magnet 3 is fixed. Between the magnet 3 and the plane portion 4a,
A spacer 5 made of a non-magnetic material such as a resin is disposed for holding the magnet 3. The magnet 3 is covered by a protective case 6 made of a non-magnetic material such as SUS for protection. After the magnet 3, the spacer 5, and the protective case 6 are mounted inside the iron bowl 4, the locking pieces 4 b provided at the ends of the iron bowl 4 are caulked toward the magnet 3, and the iron bowl 4 is secured.
Is fixed inside. In this embodiment, an example is shown in which the magnet 3 is fixed to the iron bowl 4 by caulking. However, the magnet 3 is fixed to the iron bowl 4 with an adhesive, or the magnet 3 is fixed to the iron bowl 4 by resin molding. For example, other magnet fixing means may be employed.

The boss 2 and the iron bowl 4 are fixed in the axial direction by crimping the outer peripheral end of the flange portion 2b to the inner peripheral end of the flat portion 4a. As shown in FIG. 2, a large number of groove-shaped knurls 2d extending in the axial direction are provided on the outer peripheral portion 2c of the flange portion 2b. The inner peripheral portion 4c of the flat portion 4a is provided on the outer peripheral portion 2c. By being press-fitted, the rotational force applied to the boss 2 can be reliably transmitted to the iron bowl 4 via the joining portion (the portion where the outer peripheral portion 2c and the inner peripheral portion 4c are joined). Further, the boss flange portion 2b and the iron bowl flat portion 4a are fixed in the axial direction by the press-fitting.

On one side (the right side in FIG. 1) of the outer peripheral portion 2c,
Iron bowl receiving portion 2e that receives flat portion 4a by contacting flat portion 4a of iron bowl 4 when iron bowl 4 is press-fitted by driving.
Are provided in a ring shape (see FIG. 3). The other side (the left side in FIG. 1) of the outer peripheral portion 2c is a press-fitted iron bowl 4
A caulking portion 2f for caulking the flat surface portion 4a is provided (see FIG. 4).

As shown in FIGS. 2 and 3, the caulking portion 2f has a cylindrical shape before the iron bowl 4 is caulked, and when the iron bowl 4 is caulked, as shown in FIG. The iron bowl 4 is curled toward the outer periphery and the tip is crimped. The caulking portion 2f of this embodiment is provided with a constant thickness from the root to the tip.

The outer diameter of the caulking portion 2f is provided about 0.2 to 1.5 mm inside (corresponding to the inner side of the predetermined dimension) from the outer diameter of the outer peripheral portion 2c. This value is 0.2
If it is less than mm, it becomes difficult to drive the inner peripheral portion 4c of the iron bowl 4 into the outer peripheral portion 2c of the boss 2 and press-fit it.
When the swaging section 2f is swaged as shown in FIG.
A sharp bend (small R) is generated inside the bent portion of, and stress concentration causes a problem that the swaged portion 2f is easily broken. On the other hand, if the value is larger than 1.5 mm, the swaged portion 2f
When caulking is performed as shown in FIG. 4, there occurs a problem that the force of the caulking portion 2 f pressing the iron bowl 4 is reduced.

A point P at the root of the outer peripheral side of the caulking portion 2f and starting contact with the inner peripheral portion 4c of the iron bowl 4 (see FIG. 3, corresponding to a point where the outer peripheral portion and the inner peripheral portion start contacting on the caulking portion side). )
Approximately 0.5 to 2.0 m more than the inner surface 4 d of the flat portion 4 a
m lower (corresponding to one side of a predetermined size than the other side of the iron bowl). If this value is smaller than 0.5 mm, when the swaged portion 2f is swaged as shown in FIG.
A sharp bend (small radius) inside the bent portion of the swaged portion 2f
Occurs, and the stress concentration causes a problem that the swaged portion 2f is easily broken. On the other hand, if the value is greater than 2.0 mm,
The axial dimension of the outer peripheral portion 2c, that is, the width of the outer peripheral portion 2c which is joined to the inner peripheral portion 4c of the iron bowl 4 becomes narrow, and a problem arises in that the joint strength between the boss 2 and the iron bowl 4 in the rotational direction cannot be sufficiently obtained.

As described above, a gap is provided between the caulked portion 2f of the outer peripheral portion 2c of the boss 2 and the caulked portion 2f of the inner peripheral portion 4c of the iron bowl 4 (in a state where there is no protrusion 4g). Since the outer peripheral portion 2c and the inner peripheral portion 4c are not connected to each other at the caulking portion 2f side, when an axial force as shown by an arrow A in FIG. Vibration in the direction A becomes easier. Therefore, in this embodiment, a protruding portion 4g is provided on the caulking portion 2f side of the inner peripheral portion 4c of the iron bowl 4 so as to protrude toward the inner peripheral side of the iron bowl 4 and abut on the outer peripheral surface at the root of the caulking portion 2f. .
By providing the protruding portion 4g, the outer peripheral portion 2c of the boss 2 and the inner peripheral portion 4c of the iron bowl 4 are connected to each other on the caulking portion 2f side. Therefore, even if an axial force is applied to the iron bowl 4, the iron bowl 4 can be prevented from vibrating in the direction of arrow A in FIG. 4, and as a result, the vibration resistance of the iron bowl 4 can be improved.

Further, since the protruding portion 4g provided on the iron bowl 4 is pressed at the base of the caulking portion 2f, the strength of pulling out the iron bowl 4 is improved. Further, if there is no protruding portion 4g, the tip H of the caulking portion 2f for pressing the iron bowl 4 and the caulking portion 2f
Caulking part 2 because the distance L to the root of
f is easily deformed. However, by providing the protruding portion 4g, the root portion of the caulking portion 2f is fixed by the protruding portion 4g, and the distance L from the root of the caulking portion 2f to the tip H is substantially reduced. For this reason, the force acting on the root of the caulked portion 2f is reduced, the deformation of the curled caulked portion 2f is suppressed, and the vibration resistance and the punching strength of the iron bowl 4 are improved.

The inner surface 2g of the flange portion 2b inside the root on the inner peripheral side of the caulking portion 2f is connected to the inner surface 4d of the flat portion 4a of the iron bowl 4.
Than about 0.5 to 2.0 mm lower. If this value is less than 0.5 mm, the swaged portion 2f
As shown in FIG. 4, there is a possibility that a jig (not shown) for caulking interferes with the inner surface 2g of the brim portion 2b, and the caulking portion 2f may have insufficient pushing force on the iron bowl 4. On the other hand, the value is 2.0 m
If it is larger than m, the strength at the base of the caulked portion 2f may be reduced, and the force of the caulked portion 2f pressing the iron bowl 4 may be insufficient.

As shown in FIG. 2, a relief groove 2h recessed in the inner diameter direction is formed at a corner between the outer peripheral portion 2c of the boss 2 and the iron bowl receiving portion 2e. By providing the escape groove 2h in this manner, it is possible to avoid a problem that the corner portion of the steel bowl 4 interferes with the corner R portion 4e.

The outer peripheral portion 2c of the boss 2 and the inner peripheral portion 4c of the iron bowl 4
Are provided at positions where the radial stress σ is minimum (zero). The radial stress σ is obtained by the following mathematical formula 1. A radius r at which the radial stress σ = 0 is obtained, and a joint is provided at the radius r position. It can be in the smallest position.

(Equation 1)

In the formula, a is a radius indicating the inner diameter of the iron bowl 4, b is a radius indicating the outer diameter of the boss 2, t is the thickness of the flange portion 2b, h is the thickness of the flat portion 4a, and F is the thickness of the iron bowl 4. This is the displacement of the axial vibration on the outer periphery. In this embodiment, t = h is indicated, and h and F are substituted with arbitrary constants. In addition, A and B in the equations substitute the following equations 2 and 3, respectively.

(Equation 2)

(Equation 3)

It should be noted that, instead of the above equation 1, the joining position r at the radial stress σ = 0 may be obtained by the following equation 4.

(Equation 4)

In this embodiment, an example is shown in which the joint between the boss 2 and the iron bowl 4 is provided at the position where the radial stress σ is the minimum, but the position of the joint between the boss 2 and the iron bowl 4 is described. May be provided at a position where the radial stress σ is substantially minimum. Note that the range of the substantially minimum position is 0.93 to 1.15 with respect to the radius r of the radial stress σ = 0 obtained by Expression 1 or Expression 4.
Range of double.

The position of the joint between the boss 2 and the iron bowl 4 is set at 0.
When the diameter is smaller than 93r, the radial stress σ increases, and the number of ridges formed by the knurls 2d decreases, so that the joint strength in the axial and rotational directions decreases, and the joint cannot withstand vibration from the engine side. Occur. Also, if the position of the joint between the boss 2 and the iron bowl 4 is larger than 1.15r, the diameter of the flange 2b of the boss 2 increases,
The manufacturing cost of the boss 2 increases, the advantage of joining the boss 2 and the iron bowl 4 decreases, and the radial stress σ
And the joint strength in the axial direction decreases.

Next, the operation of this embodiment having the above configuration will be described. Motorcycle engine is about 10,000 rpm
Used up to high rotations such as m. When the engine rotates at a high speed in this manner, the rotor 1 coupled to the crankshaft of the engine drives the outer peripheral side of the iron bowl 4 in the axial direction due to the dynamic imbalance and centrifugal force of the rotor 1 and drives the rotor. The outer peripheral side of the iron bowl 4 also vibrates in the axial direction due to the eccentric rotation of the shaft, and the outer peripheral side of the iron bowl 4 also vibrates in the axial direction due to the axial deviation generated when the drive shaft rotates.

When the engine rotates at a high speed and the axial vibration on the outer peripheral side of the iron bowl 4 is large, the boss 2 and the iron bowl 4 vibrate in opposite phases, and the collar 2b and the flat surface 4a ,
As shown in FIG. 1, radial stress + σ1 to -σ2 is generated. Here, the boss 2 and the iron bowl 4 have a radial stress σ =
Since the rotor is joined at the position of 0, when the rotor 1 is subjected to axial vibration, there is only a slight decrease in the pressure contact force at the joint between the boss 2 and the iron bowl 4, that is, the decrease in the axial fixing force. So even if the joint in the axial direction at the joint is caulked,
It can withstand axially enough.

The effect of this embodiment will be described. The rotor 1 of the magnet generator according to the present embodiment has a boss 2 machined from a forged product.
And the iron bowl 4 of the press-formed product are joined to form the rotor 1, so that the boss 2 and the iron bowl 4 are integrally formed by casting and finished by cutting. 1 can be significantly reduced.

The iron bowl receiving portion 2e of the boss 2 receives the iron bowl 4, and the caulking portion 2f of the boss 2 caulks the iron bowl 4 and simultaneously press-fits the outer peripheral portion 2c and the inner peripheral portion 4c of the iron bowl 4. Since the boss 2 and the iron bowl 4 are fixed in the axial direction, the boss 2 and the iron bowl 4 can be fixed in the axial direction using a press machine that is less expensive than a welding device. in this way,
Since the boss 2 and the iron bowl 4 are joined by an inexpensive press working machine as compared with the related art, the cost of the rotor 1 can be further reduced.

The outer peripheral portion 2c of the boss 2 and the inner peripheral portion 4c of the iron bowl 4
Is provided at a position where the radial stress is minimized, so that even if the rotor 1 rotates at high speed and the iron bowl 4 side vibrates in the axial direction, the joint between the boss 2 and the iron bowl 4 has a radius. Almost no directional stress is applied. For this reason, even if the structure in which the boss 2 and the iron bowl 4 are joined in the axial direction by caulking is employed, there is no problem that the joint is damaged by the axial load.

That is, the rotor 1 according to the present invention can withstand the axial load generated by the rotation of the engine with a simple structure as described above, and is inexpensive and has sufficient strength. The rotor 1 can be used.

Unlike the metal flow connection, the flat portion 4a of the iron bowl 4 does not need to be processed with a concave portion or the like for bonding. For this reason, it can join with the boss | hub 2 without lowering the intensity | strength of the plane part 4a. Therefore, when there is a request from the engine side to lower the moment of inertia of the rotor 1,
By reducing the thickness of the rotor 1, the moment of inertia can be easily reduced, and the degree of freedom in designing the rotor 1 increases.

Here, as means for finding the minimum position of the radial stress disclosed in Japanese Patent Application Laid-Open No. 60-59953, a strain gauge is attached to the plane portion of the rotor 1 and the minimum value is determined from the change in the electric resistance of the strain gauge. Means for finding the position is disclosed, but such a conventional means has a disadvantage that finding a position with the minimum radial stress requires a lot of time and money. However, in this embodiment, since the position where the radial stress is minimum is obtained by calculation, it is possible to easily find the position where the radial stress is minimum as compared with the related art.

In the first embodiment, an example in which the iron bowl receiving portion 2e is provided outside the rotor 1 and the caulking portion 2f is provided inside, however, conversely, the caulking portion 2f is provided outside the rotor 1. And an iron bowl receiving portion 2e may be provided inside.

[Second Embodiment] A second embodiment will be described with reference to FIGS. In the second embodiment, a relief groove 2h at the corner between the outer peripheral portion 2c and the iron bowl receiving portion 2e is provided in the axial direction of the iron bowl receiving portion 2e, and the corner R portion 4e of the iron bowl 4 and the corner are formed. This avoids the problem of interference with the unit. By providing the escape groove 2h on the iron bowl receiving portion 2e side in this way, the width of the outer peripheral portion 2c of the boss 2 can be increased and the length of the knurl 2d can be increased, and the press-fit amount via the knurl 2d increases. Thus, the strength of the connection between the boss 2 and the iron bowl 4 in the rotational direction and the axial direction is improved.

Third Embodiment A third embodiment will be described with reference to FIGS. 7 and 8. The swaged portion 2f before being swaged to the iron bowl 4 of the third embodiment is provided wider than the swaged portion 2f of the first and second embodiments. The outer diameter of the caulking portion 2f is about 0.2 to less than the diameter of the inner peripheral portion 4c of the iron bowl 4.
It is provided on the 1.5 mm inner circumference side (corresponding to the predetermined size inner circumference side). Outer diameter of caulking portion 2f and inner peripheral portion 4c of iron bowl 4
Is smaller than 0.2 mm, the distance from the driving intersection P of the boss 2 and the iron bowl 4 to the tip of the caulking portion 2f is short, so that a large press pressure is required when performing the coking 2j described later. Cannot be used with a press machine.
If the difference is smaller than 0.2 mm, the fitting margin before driving the boss 2 and the iron bowl 4 is small, so that it is difficult to position the boss 2 and the iron bowl 4 before driving.

However, in the present embodiment, the above difference is 0.2
mm, the distance from the driving intersection of the boss 2 and the iron bowl 4 to the tip of the caulking portion 2f becomes longer, and it is possible to reduce the pressing pressure when applying the coking 2j to be described later. Caulking 2j can be formed. Further, since the difference is set to be larger than 0.2 mm, a margin for fitting before the boss 2 and the iron bowl 4 are driven can be provided, and the positioning of the boss 2 and the iron bowl 4 before the driving is facilitated. Further, if the difference is set to be larger than 1.5 mm, the protrusion 4g becomes longer, and the strength of the protrusion 4g is reduced. However, in the present embodiment, since the above difference is provided smaller than 1.5 mm, problems can be suppressed.

The height of the swaging portion 2f is provided so as to protrude from the inner surface 4d of the flat portion 4a by about 0.8 to 1.5 mm. If the protruding length of the caulking portion 2f is lower than 0.8 mm, a sufficient caulking amount cannot be obtained when performing the coking 2j described later, and the bonding strength becomes insufficient. If it is too high, the coking load will be too high.

The caulking of the iron bowl 4 by the caulking portion 2f is performed by driving the inner peripheral portion 4c of the iron bowl 4 into the outer peripheral portion 2c of the boss 2 and then moving the outer peripheral side of the caulking portion 2f over the entire circumference. 4
Apply caulking 2j to the side
The iron bowl 4 is prevented from coming off by caulking with j. By adopting the caulking by the caulking 2j as in this embodiment, the caulking unit 2 is compared with the first and second embodiments.
The shape of f can be simplified.

When the caulking 2j is not applied over the entire circumference, that is, when divided caulking is performed, the caulking portion 2f and the protruding portion 4 are formed at the portion where the caulking 2j is not applied.
g, a gap is generated, which causes a decrease in bonding strength. However, by applying the caulking 2j all around, the caulking portion 2f
It is possible to eliminate the generation of a gap between the protrusion and the projection 4g, and it is possible to prevent a decrease in bonding strength due to the generation of the gap. In this embodiment, the relief groove 2h is provided so as to be recessed in the inner diameter direction, but may be recessed in the axial direction.

Fourth Embodiment A fourth embodiment will be described with reference to FIG. The rotor 1 according to the fourth embodiment includes a clutch outer 7 of a starter clutch in addition to the boss 2 and the iron bowl 4. Clutch outer 7 used in this embodiment
Is an existing one in which a plurality of clutch elements 8 are mounted inside, and is fixed to the rotor 1 using bolts 9 (corresponding to fasteners) inserted from the inside of the rotor 1. As described above, when the existing clutch outer 7 is used, an increase in cost can be suppressed. However, the fastening position of the bolt 9 for attaching the clutch outer 7 may interfere with the position where the radial stress is minimum. .

In such a case, as shown in the fourth embodiment, in order to avoid the above-mentioned interference, the position of the joint must be provided slightly inside the position where the radial stress is minimum. Radial stress increases. Also, the clutch outer 7 acts as a weight, and the radial stress increases due to the action. These two actions increase the radial stress due to the axial load on the joint.

For this reason, the rotor 1 of the fourth embodiment is
It is provided so as to withstand an axial load of a large joint portion as compared with each of the above embodiments. More specifically, the iron bowl receiving portion 2e of the present embodiment is extended in the outer diameter direction so that the clutch outer 7
Is formed with the spigot part 2k into which the is fitted. Further, an extended iron bowl receiving portion 2e and a flat portion 4a of the iron bowl 4
Includes a bolt 9 for fixing the clutch outer 7.
A plurality of holes 21 and 4f through which (corresponding to fasteners) are inserted are provided coaxially.

Then, the clutch outer 7 is fitted into the spigot portion 2k, the iron bowl receiving portion 2e is sandwiched between the boss 2 and the clutch outer 7, and the bolt 9 is screwed into the screw hole 7a of the clutch outer 7 from the inside of the rotor 1. , Boss 2,
The iron bowl 4 and the clutch outer 7 are fastened together. With this arrangement, the iron bowl receiving portion 2e of the boss 2 is also surely subjected to the radial stress, and the radial stress applied to the joint can be reduced. For this reason, the position of the joint is provided slightly inside the position where the radial stress is minimum, and even if the clutch outer 7 acts as a weight, sufficient joint strength can be obtained at the joint.

[Fifth Embodiment] A fifth embodiment will be described with reference to FIGS. The clutch outer 7 used in the present embodiment is also an existing one, and the clutch outer 7 of the fourth embodiment is used.
Has a structure in which a plurality of clutch elements 8 are assembled, whereas the clutch outer 7 of this embodiment has three rollers 10 assembled, and the three rollers 10 constitute a clutch mechanism. is there.

The clutch outer 7 shown in this embodiment
Is a bolt 9 inserted from the outside (corresponding to a fastener)
The clutch outer 7 is formed with a spigot portion 7 b fitted to the rotor 1. The present embodiment is provided such that the existing clutch outer 7 is used and the joint between the boss 2 and the iron bowl 4 has a minimum radial stress. Specifically, the shape of the flange portion 2b is provided so as to fit into the spigot portion 7b of the clutch outer 7, and the portion of the flange portion 2b into which the bolt 9 is screwed is provided thickly. It is provided so as to avoid the problem of interfering with the joint.

With this arrangement, the load of the clutch outer 7 is applied only to the boss 2 and the joint is provided at the position where the stress in the radial direction is minimum, so that the iron bowl is provided as shown in the fourth embodiment. It is not necessary to reinforce with the receiving portion 2e, and even in the case where the clutch outer 7 is provided, as shown in the first to third embodiments, the axial strength can be ensured only by the joint portion.

[Sixth Embodiment] A sixth embodiment will be described with reference to FIG. In the sixth embodiment, the swaged portion 2f before being swaged to the iron bowl 4, that is, the swaged portion 2f having a tubular shape.
Are provided in a tapered shape that becomes thinner toward the front end. With this provision, the swaged portion 2f is easily deformed in the radial direction toward the front end.
When caulking f to the iron bowl 4, the caulked portion 2f can be easily curled, and the productivity is improved.

Seventh Embodiment A seventh embodiment will be described with reference to FIG. In the seventh embodiment, the relief groove 2h at the corner between the outer peripheral portion 2c and the iron bowl receiving portion 2e is provided so as to be commonly recessed in both the inner diameter direction and the axial direction. Such a relief groove 2h can be easily formed by rotating the boss 2 and pressing a cutting tool against a corner portion of the rotating boss 2. For this reason, the productivity of the relief groove 2h is superior to the case where the relief groove 2h is formed only in the inner diameter direction or only in the outer diameter direction.

[Brief description of the drawings]

FIG. 1 is a sectional view of a rotor (first embodiment).

FIG. 2 is a perspective view of an outer peripheral portion of a boss (first embodiment).

FIG. 3 is a perspective view of a joining portion in a state before the caulking portion caulks an iron bowl (first embodiment).

FIG. 4 is a perspective view of a joining portion in a state where the caulking portion is caulking an iron bowl (first embodiment).

FIG. 5 is a perspective view of an outer peripheral portion of a boss (second embodiment).

FIG. 6 is a perspective view of a joining portion before a caulking portion caulks an iron bowl (second embodiment).

FIG. 7 is a perspective view of a joining portion in a state before a caulking portion caulks an iron bowl (third embodiment).

FIG. 8 is a perspective view of a joining portion in a state where the caulking portion is caulking an iron bowl (third embodiment).

FIG. 9 is a sectional view of a rotor having a clutch outer (fourth embodiment).

FIG. 10 is a sectional view of a rotor having a clutch outer (fifth embodiment).

FIG. 11 is a perspective view of a joining portion in a state where the caulking portion is caulking an iron bowl (fifth embodiment).

FIG. 12 is a perspective view of a joining portion in a state before a caulking portion caulks an iron bowl (sixth embodiment).

FIG. 13 is a perspective view of a joining portion in a state before the caulking portion caulks an iron bowl (seventh embodiment).

[Explanation of symbols]

Reference Signs List 1 rotor 2 boss 2c outer peripheral part 2d knurl 2e iron bowl receiving part 2f caulking part 2h escape groove 2j caulking 2k spigot part 2n screw hole 3 permanent magnet 4 iron bowl 4c inner peripheral part 4g projecting part 7 clutch outer 7b spigot part 9 bolt (Fastener) Point P (the point where the outer and inner circumferences start to contact on the swaged side)

Claims (12)

[Claims] 1. A rotation of a magnet generator comprising a boss fixed to a rotary drive shaft and an iron bowl disposed concentrically on the outer periphery of the boss and having a permanent magnet disposed on an inner peripheral surface thereof. The outer peripheral portion of the boss and the inner peripheral portion of the iron bowl are in contact with each other, and the iron bowl hits an iron bowl receiving portion provided on one side of the outer peripheral portion, and further on the other side of the outer peripheral portion. The boss and the iron bowl are fixed in the axial direction by the provided caulking part caulking the iron bowl, and the joint between the outer peripheral part and the inner peripheral part is formed in a radial direction by an axial load. Wherein the tensile stress is provided at a position where the tensile stress is substantially minimum. 2. The rotor of the magnet generator according to claim 1, wherein the outer diameter of the caulking portion is provided on the inner side of a predetermined dimension from the outer diameter of the outer portion, and the outer peripheral portion and the inner periphery are provided. The point at which the part starts to contact on the caulking part side is provided on the one side of a predetermined size from the other surface of the iron bowl, and the caulking part side of the inner peripheral part of the iron bowl is the iron bowl. A rotor of a magnet generator, wherein a protruding portion is provided which protrudes to the inner peripheral side of the outer peripheral surface and abuts on the outer peripheral surface at the base of the caulking portion. 3. The rotor of the magnet generator according to claim 1 or 2, further comprising a clutch outer of a starter clutch in addition to the boss and the iron bowl, wherein the iron bowl receiving portion has an outer diameter direction. And a spigot portion into which the clutch outer is fitted is formed.The spigot receiving portion is sandwiched between the spigot and the clutch outer in a state where the clutch outer is fitted into the spigot portion. The rotor of the magnet generator, wherein the boss, the iron bowl and the clutch outer are fastened together by a fastener in a state. 4. The rotor of a magnet generator according to claim 1, further comprising a clutch outer for a starter clutch, in addition to the boss and the iron bowl, wherein the clutch outer is provided on one surface. A spigot portion into which the boss is fitted is formed, and in a state where the spigot portion is fitted to the boss, the spigot portion is fastened to a screw hole provided in the boss from the clutch outer side using a fastener. Characteristic rotor of magnet generator. 5. The rotor of the magnet generator according to claim 1, wherein the outer peripheral portion is provided with a number of groove-shaped knurls extending in an axial direction, and the inner peripheral portion is provided with a plurality of grooves. Is press-fitted into the outer peripheral portion where the knurl is provided, wherein the rotor is a magnet generator. 6. The rotor for a magnet generator according to claim 1, wherein the caulking portion has a cylindrical shape before caulking the iron bowl, and caulks the iron bowl. In this case, the rotor of the magnet generator is curled to the outer peripheral side and the tip end portion is caulked of the iron bowl. 7. The rotor of the magnet generator according to claim 6, wherein the caulked portion having a cylindrical shape before being caulked to the iron bowl is provided with a constant thickness from a root to a tip. A rotor of a magnet generator. 8. The rotor of the magnet generator according to claim 6, wherein the caulking portion having a tubular shape before being caulked to the iron bowl is provided in a tapered shape that becomes thinner toward the tip. And the rotor of the magnet generator. 9. The rotor of the magnet generator according to claim 1, wherein the caulking portion has a tubular shape before caulking the iron bowl, and caulks the iron bowl. In this case, the iron bowl is caulked by caulking in which an outer peripheral side is crushed toward the iron bowl side. 10. The rotor of the magnet generator according to claim 1, wherein a relief groove recessed in an inner diameter direction is formed at a corner between the outer peripheral portion and the iron bowl receiving portion. A rotor for a magnet generator. 11. The rotor of the magnet generator according to claim 1, wherein a corner between the outer peripheral portion and the iron bowl receiving portion is recessed in an axial direction of the iron bowl receiving portion. A rotor for a magnet generator, wherein a relief groove is formed. 12. The rotor of the magnet generator according to claim 1, wherein a corner portion between said outer peripheral portion and said iron bowl receiving portion has an inner diameter direction and said iron bowl receiving portion. A rotor for a magnet generator, wherein a common relief groove recessed in both the axial direction is formed.