JP2008048497A - Variable air-gap rotary electric machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To propose a variable air-gap rotary electric machine wherein an air gap can be varied by a slight force. <P>SOLUTION: The variable air-gap rotary electric machine is of axial gap type and is so constructed that a rotor 1 is disposed opposed to a stator in the direction of an axis O. The opposite faces 3 can be moved in the direction of the axis O. Of the rotor core 5 having the opposite face 3, the outer radius portion and the inner radius portion are different from each other in the amount of movement in the axial direction. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a variable air gap type rotating electrical machine that can change a gap (air gap) between a rotor that is a rotor and a stator that is a stator.

A gap between the rotor and the stator is called an air gap, and becomes a magnetic resistance of a magnetic circuit formed between the rotor and the stator in order to drive the rotor. As an axial gap type rotating electrical machine capable of arbitrarily changing the air gap according to the operating state of the rotating electrical machine, such as when the rotor rotates at high speed, conventionally, for example, the one described in Patent Document 1 is known. Yes.
In the axial gap type rotating electrical machine described in Patent Document 1, the gap between the stator and the rotor, that is, the gap of the air gap is changed by an actuator such as a counter pendulum.
Japanese Patent Laid-Open No. 2002-325412

  However, the conventional axial gap type rotating electrical machine has the following problems. That is, since the entire rotor is translated in the axial direction against the magnetic force between the rotor and the stator, the actuator needs to apply a large force to the rotor. If it does so, an actuator will enlarge, the problem which the mounting property of the said axial gap type rotary electric machine will be restrained will arise, and a weight will increase.

  In view of the above circumstances, the present invention proposes an axial gap type variable air gap type rotating electrical machine capable of moving a rotor with a small force.

For this purpose, the variable air gap type rotating electrical machine according to the present invention is as described in claim 1,
An axial gap type rotating electrical machine in which the stator and the rotor are arranged to face each other in the axial direction, and the variable air gap type rotating electrical machine in which the facing surfaces facing each other are movable in the axial direction.
Among the members having the opposed surfaces, the axial movement amount of the outer diameter side portion and the axial movement amount of the inner diameter side portion are different from each other.

  According to the configuration of the present invention, when moving the facing surface member of either the rotor or the stator so that the air gap formed between the facing surface of the rotor and the facing surface of the stator changes, Since the amount of axial movement at the outer diameter side portion of the surface member is different from the amount of axial movement at the inner diameter side portion of the facing surface member, the facing surface member moves or tilts non-parallel to the rotation axis. For this reason, with a slight force, it is possible to move or incline the opposing surface member non-parallel, and a variable air gap type rotating electrical machine can be realized with a small actuator. Therefore, unlike the prior art, it is not necessary to translate the entire opposing surface component in the axial direction with a large force, and the problems such as the above-mentioned problem that the mountability of the rotating electrical machine is restricted and the increase in weight are solved. Can do.

Hereinafter, embodiments of the present invention will be described in detail based on examples shown in the drawings.
FIG. 1 is a longitudinal sectional view showing a state in which a variable air gap type rotating electrical machine according to a first embodiment of the present invention is cut along a plane including a rotating shaft.
In FIG. 1, 1 indicates a rotor. The rotor 1 has a disk shape and rotates about an axis O represented by a one-dot chain line. A rotor shaft 2 extending along the axis O is provided in the center of the rotor 1. The rotor shaft 2 takes out the rotation of the rotor 1. A stator indicated by a broken line is arranged in the vicinity of the axis O direction of the rotor 1, and the rotor 1 and the stator are opposed to each other to form a rotating electrical machine having an axial gap structure.

  An air gap 4 (gap) is formed between the facing surface 3 facing the stator on the surface of the rotor 1 and the facing surface of the stator. As shown in FIG. 1, the rotor facing surface 3 is normally in a direction perpendicular to the axis O, and the opposed surfaces of the stator are also perpendicular to the axis O, and these opposed surfaces are parallel to each other. However, due to the axial movement of the rotor facing surface 3 described later, the rotor facing surface 3 and the opposed surface of the stator are appropriately non-parallel, and the distance between the rotor 1 and the stator changes.

  A rotor core 5 is disposed on the rotor facing surface 3. A disc-shaped rotor base 6 is disposed on the back surface of the rotor 1 that is not opposed to the stator. The rotor base 6 is connected to the rotor shaft 2 at the center, and supports the rotor core 5 on the surface close to the stator.

The rotor core 5 has a structure in which thin steel plates 7 are laminated in the radial direction, and constitutes the facing surface 3. A plurality of permanent magnets (not shown) are arranged on the rotor core 5 at regular intervals in the circumferential direction when viewed from the axis O. Further, the rotor core 5 is provided with a plurality of holes extending in the radial direction at equal intervals in the circumferential direction when viewed from the axis O, and rod-shaped reinforcing members 8 are respectively passed through these holes. That is, as shown in FIG. 1, the reinforcing member 8 penetrates the steel plate 7 laminated in the radial direction, that is, the direction perpendicular to the axis O in the radial direction so that the steel plate 7 does not loosen in the direction of the axis O. Preferably, the surface of the reinforcing member 8 is covered with a material having high electrical resistance. This is to prevent an electrical short circuit between the steel plates 7 and 7. Further, it is preferably coated with a material having a low coefficient of friction. This is because the frictional resistance is reduced between the reinforcing member 8 and the steel plate 7 to smooth the deformation of the rotor core 5. Specifically, the reinforcing member 8 is covered with Teflon (registered trademark) or the like.
The radially outer end of the rotor core 5 is supported by the outer peripheral edge 9 of the rotor base 6. Further, the radially inner end of the rotor core 5 is supported by the central portion 10 of the rotor base 6. Since the steel plate 7 is interposed between the outer peripheral edge portion 9 and the center portion 10 of the rotor base 6, the steel plate 7 is not loosened in the radial direction.

  A gap 11 is provided in the rotor core 5 and the rotor base 6 between the rotor base peripheral portion 9 and the rotor base central portion 10.

  The rotor base peripheral portion 9 is hinge-coupled to the radially outer end of the reinforcing member 8 described above. The rotor base center portion 10 is provided with a hole 12 extending in the radial direction, and the inner diameter side portion of the reinforcing member 8 is passed through the hole 12. The hollow section of the hole 12 is larger than the cross section of the reinforcing member 8, and there is a gap in the direction of the axis O between the inner periphery of the hole 12 and the outer periphery of the reinforcing member 8 as shown in FIG.

  A piston mechanism is interposed between the rotor base central portion 10 and the rotor shaft 2. The inner end of the reinforcing member 8 is hinged to the piston 13 of this piston mechanism.

  A disc spring 15 is interposed between the rotor base 6 and the piston 13, and the disc spring 15 holds the piston 15 in the normal position shown in FIG. The piston 13 partitions the liquid chamber 14 between the rotor shaft 2 and the rotor shaft 2. The liquid chamber 14 is connected to a pipe line 16 provided inside the rotor shaft 2, and exchanges hydraulic fluid from the pipe line 16.

FIG. 2 is a longitudinal sectional view showing a state in which the piston 13 is axially moved away from the air gap 4 from the normal position shown in FIG. When the hydraulic fluid flows into the liquid chamber 14, the liquid chamber 14 expands and the piston 13 moves in the axial direction so as to move away from the air gap 4 while pushing the disc spring 15. Along with this, the inner diameter side end of the reinforcing member 8 also moves axially away from the air gap 4. At the same time, the inner diameter side portion of the reinforcing member 8 also moves in the hole 12 in the axial direction.
In contrast, the outer diameter side end of the reinforcing member 8 does not move in the direction of the axis O while being hinged to the rotor base 6. Thus, when the inner diameter side end of the reinforcing member 8 moves in the axial direction so as to be different from the outer diameter side end, the reinforcing member 8 is inclined, and the rotor core 5 narrows the air gap 11 as shown in FIG. Move axially away from As described above, the piston 13 can move the inner diameter side portion of the rotor core 5 in the direction of the axis O with a slight force, and the amount of axial movement of the facing surface 3 of the rotor core 5 is determined between the outer diameter side portion and the inner diameter side portion. Therefore, the air gap 4 can be widened.

  When attention is paid to the steel plate 7 of the rotor core 5, in the normal state shown in FIG. 1, there is no deviation in the axis O direction between the steel plates adjacent in the radial direction. However, as the reinforcing member 8 is tilted as shown in FIG. 2, a slight shift in the axis O direction occurs between the steel plates adjacent in the radial direction.

  Accordingly, the reinforcing member 8 is provided, or in place of the reinforcing member 8, the uneven shape shown in FIGS. 3 and 4 is provided on the steel plate 7 to appropriately prevent the slight deviation in the axis O direction that occurs between the steel plates adjacent in the radial direction. The axial movement of the rotor core 5 may be realized.

  FIG. 3 is an enlarged view of the portion of the steel plate 7 indicated by a two-dot chain line in the rotor core 5 shown in FIG. A concave portion 7a having an axial width W1 is formed on one surface of the steel plate 7. A convex portion 7b having an axial width W2 narrower than the concave portion 7a is formed on the other surface. And these recessed part 7a and the convex part 7b are engaged. As shown in FIG. 3, the convex part 7b is located in the left side in the figure of the concave part 7a.

  FIG. 4 is an enlarged view showing a portion of the steel plate 7 indicated by a two-dot chain line in the rotor core 5 shown in FIG. When the rotor core 5 moves in the axial direction, the adjacent steel plates 7 shift to the length of W1-W2 in the axial direction, and the convex portion 7b moves to the right side of the concave portion 7a as shown in FIG.

  As shown in FIGS. 3 and 4, the axial movement of the convex portion 7a is restricted within the concave portion 7a. Therefore, by providing the concave and convex engaging portions 7a and 7b. The axial movement of the adjacent steel plates 7 and 7 can be defined as the difference between the axial width of the concave portion 7a and the axial width of the convex portion 7b, and the axial direction of the rotor core 5 in which the steel plates 7 are laminated in the radial direction. The movement can be defined within the range shown in FIGS. As a result, the axial movement amount of the outer diameter side portion of the rotor core 5 and the axial movement amount of the inner diameter side portion can be different.

  In order to return the piston 13 from the position shown in FIG. 2 to the normal position shown in FIG. 1, the hydraulic fluid flows out from the liquid chamber 14 to contract the liquid chamber 14, and the disc spring 15 pushes the piston 13 back. 13 moves in the axial direction so as to approach the air gap 4.

Next, a second embodiment of the present invention will be described.
FIG. 5 is a longitudinal sectional view of the rotor 1 according to the second embodiment, and shows a normal position of the rotor core 5.
This second embodiment also relates to an axial gap type rotating electrical machine in which the rotor 21 and the stator are arranged opposite to each other in the axis O direction of the rotor 1. Therefore, about the structure which is common in 1st Example mentioned above, the same code | symbol is attached | subjected and description is abbreviate | omitted and a different structure is demonstrated.
In the second embodiment shown in FIG. 5, the piston mechanism is provided not on the inner diameter side portion of the rotor core 5 but on the outer diameter side portion. The piston 13 of the piston mechanism is connected to the outer diameter side portion of the rotor core 5 and partitions the liquid chamber 14 with the rotor base 6. The piston 13 moves in the direction of the axis O by the expansion and contraction of the liquid chamber 14.
A pipe line 22 is provided inside the rotor base 6, and the pipe line 22 connects the pipe line 16 and the liquid chamber 14 inside the rotor shaft 2.

  Also in the second embodiment shown in FIG. 5, the piston 13 can move the outer diameter side portion of the rotor core 5 in the direction of the axis O with a slight force, and the axial movement of the facing surface 3 of the rotor core 5. The air gap 4 can be widened by the amount being different between the outer diameter side and the inner diameter side.

The first embodiment in which the inner diameter side portion of the rotor core 5 is attached to the rotor base 6 so as to be movable in the axial direction and the outer diameter side portion of the rotor core 5 are attached to the rotor base 6 so as to be movable in the axial direction. The second embodiment will be described in comparison with a conventional example in which the entire rotor core is moved.
FIG. 6 is a characteristic diagram showing the relationship between the axial movement amount of the rotor core and the axial force necessary for the movement. In FIG. 6, the horizontal axis indicates the amount of axial movement, and the vertical axis indicates the axial force.
In the conventional example of moving the entire rotor core, a large axial force is required regardless of the amount of axial movement.
In the second embodiment in which the outer diameter side portion of the rotor core 5 is moved, the rotor core 5 can be moved with a smaller axial force than in the conventional example regardless of the amount of axial movement.
In the first embodiment in which the inner diameter side portion of the rotor core 5 is moved, the rotor core 5 can be moved with a smaller axial force than the conventional example regardless of the amount of axial movement.

  Therefore, a variable air gap type rotating electrical machine can be realized by using a small piston mechanism or actuator, and the problem of improving the mountability of the rotating electrical machine and increasing the weight can be solved.

Next, a third embodiment of the present invention will be described.
FIG. 7 is a longitudinal sectional view of the rotor 1 according to the third embodiment, and shows the normal position of the rotor core 5.
This third embodiment also relates to an axial gap type rotating electrical machine in which the rotor 31 and the stator are arranged to face each other in the axis O direction of the rotor 1. Therefore, about the structure which is common in 1st Example mentioned above, the same code | symbol is attached | subjected and description is abbreviate | omitted and a different structure is demonstrated.
In the third embodiment shown in FIG. 7, the piston mechanism is provided on the outer diameter side portion of the rotor core 5. The piston 13 of the piston mechanism is connected to the outer diameter side portion of the rotor core 5 and partitions the liquid chamber 14 with the rotor base 6. The piston 13 moves in the direction of the axis O by the expansion and contraction of the liquid chamber 14. The rotor core 5 made of the steel plate 7 is provided with a hole extending in the radial direction, and a hollow member 32 made of an elastic material is passed through the hole. That is, as shown in FIG. 1, the hollow member 32 penetrates the steel plate 7 laminated in the radial direction, that is, the direction perpendicular to the axis O in the radial direction so that the steel plate 7 does not loosen in the direction of the axis O. The steel plate 7 is provided with the concavo-convex shapes 7a and 7b described above with reference to FIGS.

  The liquid chamber 14 of the piston mechanism at the outer diameter side portion of the rotor core 5 connects the radially outer end of the hollow member 32. The radially inner end of the hollow member 32 is connected to the pipe line 16 provided inside the rotor shaft 2.

  By transferring the hydraulic fluid from the pipe line 16 to the fluid chamber 14 of the piston mechanism via the hollow member 32, the piston 13 moves in the direction of the axis O, and the outer diameter side portion of the rotor core 5 is pivoted with respect to the rotor base 6. Move in the direction. FIG. 5 shows the normal positions of the rotor core 5 and the piston 13. When the working fluid flows into the liquid chamber 14, the liquid chamber 14 expands and the piston 13 moves in the axial direction to the left in the figure while pushing the disc spring 15 from the normal position. Along with this, the outer diameter side portion of the rotor core 5 moves away from the stator (not shown) while narrowing the gap 11. As described above, the rotor core 5 and the rotor facing surface 3 move in the axial direction, and the air gap 4 is widened.

  Also in the third embodiment shown in FIG. 7, the piston 13 can move the outer diameter side portion of the rotor core 5 in the direction of the axis O with a slight force, and the axial movement of the opposing surface 3 of the rotor core 5. The air gap 4 can be widened by the amount being different between the outer diameter side and the inner diameter side.

Next, a fourth embodiment of the present invention will be described.
FIG. 8 is a longitudinal sectional view of the rotor 1 according to the fourth embodiment, and shows a normal position of the rotor core 5.
The fourth embodiment also relates to an axial gap type rotating electrical machine in which the rotor 41 and the stator are arranged to face each other in the direction of the axis O of the rotor 1. Therefore, about the structure which is common in 1st Example mentioned above, the same code | symbol is attached | subjected and description is abbreviate | omitted and a different structure is demonstrated.
In the fourth embodiment shown in FIG. 8, the central portion of the rotor base 42 that attaches the rotor base 42 to the rotor shaft 2 so as to be movable in the axial direction serves as the piston of the piston mechanism, and is located between the enlarged diameter portion 44 of the rotor shaft 2. The liquid chamber 14 is partitioned. The rotor base 42 moves in the direction of the axis O by the expansion and contraction of the liquid chamber 14. A disc spring 15 on the surface of the rotor base 42 that is far from the liquid chamber 14, that is, the back surface of the rotor 41, and a retaining member that prevents the disc spring 15 and the rotor base 42 from coming out of the rotor shaft 2. The nuts 43 are sequentially attached.

The outer peripheral edge 45 of the rotor base 42 supports the outer diameter side portion of the rotor core 5.
The inner diameter side portion of the rotor core 5 is supported by the enlarged diameter portion 44 of the rotor shaft 2.
Since the steel plate 7 of the rotor core 5 is interposed between the outer peripheral edge portion 45 of the rotor base 42 and the enlarged diameter portion 44 of the rotor shaft 2, the steel plate 7 is not loosened in the radial direction.

  When the hydraulic fluid flows into the liquid chamber 14, the liquid chamber 14 expands, and the rotor base 42 and the outer peripheral edge 45 push the disc spring 15 and move away from the air gap 4 while expanding the gap 11 as shown in FIG. 9. To do. Along with this, the radially outer end of the reinforcing member 8 moves away from the air gap 4. Since the radially inner end of the reinforcing member 8 is attached to the enlarged diameter portion 44 of the rotor shaft 2, the amount of movement in the axis O direction differs at both ends, and the reinforcing member 8 is inclined. The rotor core 5 through which the reinforcing member 8 penetrates moves axially away from the air gap 4. From the above, the rotor base 42 can move the outer diameter side portion of the rotor core 5 in the direction of the axis O with a slight force, and the axial movement amount of the opposed surface 3 of the rotor core 5 is the outer diameter side portion and the inner diameter side. The air gap 4 can be widened by being different from each other.

As shown in FIGS. 8 and 9, a friction clutch fastening member 46 is attached to the back surface of the rotor base 42, and a fastened member 47 is disposed on the side far from the friction fastening member 46 when viewed from the air gap 4. . In the normal position where the air gap 4 is not changed, as shown in FIG. 8, the rotor 41 and the fastened member 47 are separated from each other, and the both 41 and 47 are not fastened.
On the other hand, in a state where the air gap 4 is widened, as shown in FIG. 9, the frictional fastening member 46 comes into contact with the fastened member 47, and the rotor 41 is fastened with the fastened member 47.

FIG. 10 is a longitudinal sectional view showing an application example in which the rotating electric machine of the fourth embodiment described above is combined with a clutch and a brake provided on a drive transmission path for taking out the driving force of the rotating electric machine.
A sun gear 51 s of the planetary gear set 51 is coupled to the tip of the rotor shaft 2. The carrier 51c of the planetary gear set 51 is coupled to an output shaft 52 provided on the side opposite to the rotor shaft 2 when viewed from the planetary gear set 51. A friction clutch 53 is inserted between the sun gear 51s and the carrier 51c. A friction brake 55 is inserted between the ring gear 51r of the planetary gear set 51 and a fixing member 54 such as a reduction gear case. This configuration is used as a vehicle power train.

  The friction clutch 53 is disposed in the vicinity of the rotor 41. A protrusion 48 is provided on the back surface of the rotor 41. As shown in FIG. 10, since the air gap 4 is normally set small, the rotor base 42 is located on the left side of the stator 49 in FIG. 10 and is separated from the friction clutch 53. Therefore, a gap 56 is generated between the protrusion 48 and the friction clutch 53. The air gap 56 prevents heat from reaching the rotor 41 from the planetary gear set 51 side. The friction clutch 53 is released. At the same time, the friction brake 55 is fastened by an attached actuator 57. Then, the rotation speed of the carrier 51c is less than the rotation speed of the sun gear 51s, and the rotation of the rotor 41 is decelerated and transmitted to the output shaft 52. Since the air gap 4 is small, the torque output from the rotor 41 is large.

  When the hydraulic fluid is supplied to the fluid chamber 14 and the air gap 4 is widened as described above with the friction brake 55 engaged, the rotor base 42 moves to the friction clutch 53 side on the right side in FIG. During this movement, the protrusion 48 is not pressed against the friction clutch 53 although the gap 56 is narrowed. Then, although the carrier 51c and the sun gear 51s, which are the friction clutch fastening member and the non-fastening member, are released, the torque of the rotor 41 decreases as the air gap 4 widens. That is, the torque of the rotor 41 is smaller than that in the above-described deceleration state, and the rotation of the rotor 41 is decelerated and transmitted to the output shaft 52.

  When the hydraulic fluid is sufficiently supplied to the liquid chamber 14 and the rotor base 42 is completely moved to the friction clutch 53 side, the friction clutch 53 is completely engaged, and the engagement is completed between the carrier 51c and the sun gear 51s. At the same time, the friction brake 55 is released by the attached actuator 57. If it does so, the rotation speed of the carrier 51c will correspond with the rotation speed of the sun gear 51s, and it will be in a direct connection state. Since the air gap 4 is large, the torque output from the rotor 41 is small in the direct connection state.

When represented by the relationship between the deceleration state, the transient state, and the direct connection state, the graph shown in FIG. 11 is obtained. In FIG. 11, the horizontal axis represents the vehicle speed [km / h] and is equivalent to the rotational speed [rpm] of the output shaft 52. In FIG. 11, the vertical axis represents the driving force [N] of the output shaft 52.
According to the embodiment shown in FIG. 10, the driving torque of the output shaft 52 can be increased in the deceleration state, and the driving torque of the output shaft 52 can be decreased in the transient state. Further, when the switching operation from the deceleration state to the direct connection state through the transient state is performed, or when the switching operation is performed in the opposite direction, the driving torque of the output shaft 52 can be appropriately controlled. Further, since the rotor base 42 not only adjusts the air gap 4 but also serves as an actuator of the friction clutch 53, it can contribute to saving of parts space and the number of parts, which is advantageous in terms of cost. It becomes.
In addition to the embodiment shown in FIG. 10, although not shown in the drawing, the engagement release pattern of the friction clutch 53 and the friction brake 55 is changed by changing the shape of the protrusion 48 or changing the size of the gap 56. Can be realized in various variations.

By the way, according to the above-described embodiments, the rotor core 5 having the facing surface 3 is configured such that the axial movement amount of the outer diameter side portion and the axial movement amount of the inner diameter side portion are different from each other. Thus, the air gap 4 can be changed without translating the entire rotor core 5. Therefore, it is possible to realize a variable air gap type rotating electrical machine using a slight force, and it is possible to reduce the size and labor of an actuator such as a piston mechanism. In addition, it is possible to eliminate adverse effects such as an increase in the weight of the rotating electrical machine and the space occupied by the parts.
In addition, since it is only necessary to move the opposing surface member of either the rotor or the stator non-parallel to the axis O, as described above, the rotor core 5 constituting the rotor-side facing surface 3 of the air gap 4 is moved, Although not shown in the drawings, the members constituting the stator side facing surface of the air gap 4 are configured such that the axial movement amount of the outer diameter side portion and the axial movement amount of the inner diameter side portion of the members are different. Of course, you may do.

  Specifically, in the first embodiment, of the rotor core 5 of the rotor 1 that is a member constituting the facing surface 3, the rotor core outer diameter side portion is attached to the rotor base 6 of the rotor 1 so as not to be axially movable, and the rotor core inner diameter is Since the side portion is attached to the rotor base 6 through the piston 13 so as to be movable in the axial direction, the rotor core 5 that is the opposing surface member can be moved in the axial direction with a slight force. This makes it possible to eliminate the adverse effects of increasing the weight of the rotating electrical machine and the space occupied by the parts. Further, since the piston mechanism is provided on the inner diameter side, the pipe line 16 can be easily routed from the rotor shaft 2 to the liquid chamber 14.

In the second and third embodiments, the rotor core inner diameter side portion of the rotor cores 5 of the rotors 21 and 31 which are members constituting the facing surface 3 cannot be moved axially to the rotor base 6 of the rotors 21 and 31. Since the rotor core outer diameter side portion is attached to the rotor base 6 via the piston 13 so as to be axially movable,
When a piston mechanism is employed as the actuator, the piston area and the like can be increased on the outer diameter side having a long circumference, and the radial dimension of the piston mechanism can be shortened.

Further, in the fourth embodiment, of the rotor core 5 of the rotor 41 that is a member constituting the facing surface 3, the rotor core inner diameter side portion is attached to the rotor shaft 2 of the rotor 41 so as not to be axially movable, and the rotor core outer diameter side portion is attached. Since it is attached to the rotor base 42 of the rotor 41 and the rotor base 42 is attached to the rotor shaft 2 so as to be axially movable,
It is possible to move the rotor core 5, which is a facing member, in the axial direction with a slight force, thereby reducing the size and labor of actuators such as piston mechanisms, and increasing the weight of the rotating electrical machine and the space occupied by parts. Can be resolved. Further, the axial movement of the rotor base 42 can be used as a separate actuator.

  As an embodiment in which the variable air gap type rotating electrical machine of the fourth embodiment is applied, at least one of a friction clutch 53 and a friction brake 55 is provided on the drive transmission path of the rotor 41 as shown in FIG. Since the friction clutch 53 is configured to be engaged and released using movement in the O direction, the rotor base 42 not only adjusts the air gap 4 but also serves as an actuator for the friction clutch 53, thereby reducing the parts space. This contributes to a reduction in the number of parts and the number of parts, which is advantageous in terms of cost.

  In the first to fourth embodiments, the rotor core 5 is obtained by laminating the steel plates 7 in the radial direction, and includes a permanent magnet. Therefore, the variable air gap technique according to the present invention is permanently applied to the rotor. The present invention can be applied to a permanent magnet motor using a magnet, and has a unique effect that the air gap changes while the rotor core 5 is deformed. Further, the coupling between the actuator such as the piston 13 and the rotor core 5 can be made soft, and it is possible to avoid the occurrence of excessive deformation or stress at the coupling portion during the air gap change.

  Further, a hole extending in the radial direction is provided in the rotor core 5 made of the steel plate 7, and the reinforcing member 8 is passed through the hole, and one of the inner diameter side end portion and the outer diameter side end portion of the reinforcing member 8 is the rotor base. Since the other is attached to the rotor base 6 via the piston 13 so as to be movable in the axial direction, the air gap 4 can be changed by shifting the steel plate 7 in the axis O direction.

As shown in FIG. 3 and FIG. 4 as a structure in which the rotor core 5 is deformed, a recess 7 a is provided on one surface of the surfaces where the outer diameter side steel plate 7 and the inner diameter side steel plate 7 are in contact with each other, and the other surface Is provided with a convex portion 7b, and the concave and convex portions 7a and 7b are engaged with each other. The concave and convex portions 7a and 7b change the axial movement of the rotor core 5, and the difference in the axial width of the concave and convex portions 7a and 7b ( Specified range),
The amount of axial movement of the outer diameter side portion of the rotor core 5 can be different from the amount of axial movement of the inner diameter side portion, and the air gap 4 is changed by moving the facing surface 3 non-parallel to the stator. can do. Further, there is no concern that the air gap 4 is undesirably narrowed because the radial center of the rotor core is bent in the stator direction, and the air gap can be easily managed.

Further, as in the third embodiment shown in FIG. 7, a hole extending in the radial direction is provided in the rotor core 5 made of the steel plate 7, and the hollow member 32 made of an elastic material is passed through the hole, so A piston mechanism that moves in the axial direction is provided between the rotor base 6 and the rotor base 6. The liquid chamber 14 of the piston mechanism is connected to the radially outer end of the hollow member 32, and passes through the radially inner end of the hollow member 32. Since the piston 13 moves the outer diameter side portion of the rotor core 5 in the axial direction with respect to the rotor base 6 by transferring the hydraulic fluid to the liquid chamber 14 of the piston mechanism.
The air gap 4 can be changed by moving the facing surface 3 non-parallel to the stator. In addition, since the elastic material is used, the above-described hinge connection is not necessary in the connection between the actuator such as the piston 13 and the rotor core 5, and the mechanism can be simplified. And backlash can be reduced in the said connection location and the adjacent steel plates 7. FIG. Further, since the hollow member also serves as a pipe line, the part space and the number of parts can be reduced.

  The above description is merely an example of the present invention, and the present invention can be variously modified without departing from the spirit of the present invention.

It is a longitudinal cross-sectional view which shows the state which cut | disconnected the rotor of the variable air gap type rotary electric machine which becomes 1st Example of this invention by the plane containing a rotating shaft. In the same Example, it is a longitudinal cross-sectional view which shows the state which the air gap changed. It is a longitudinal cross-sectional view which expands and shows the uneven | corrugated engagement shape provided in the steel plates adjacent in radial direction, and shows the normal state in which a rotor core opposing surface is parallel with respect to a stator. It is a longitudinal cross-sectional view which shows the state after the air gap change from which the steel plate mutually shift | displaces to an axial direction, and a rotor core opposing surface becomes non-parallel with respect to a stator. It is a longitudinal cross-sectional view which shows the state which cut | disconnected the rotor of the variable air gap type rotary electric machine which becomes 2nd Example of this invention by the plane containing a rotating shaft. It is a characteristic view which shows the relationship between the axial direction movement amount of a rotor core, and the axial direction force required for the said movement. It is a longitudinal cross-sectional view which shows the state which cut | disconnected the rotor of the variable air gap type rotary electric machine which becomes 3rd Example of this invention by the plane containing a rotating shaft. It is a longitudinal cross-sectional view which shows the state which cut | disconnected the rotor of the variable air gap type rotary electric machine which becomes 4th Example of this invention by the plane containing a rotating shaft. In the same Example, it is a longitudinal cross-sectional view which shows the state which the air gap changed. It is a longitudinal cross-sectional view which shows the application example combined with the rotary electric machine of the Example, and the clutch and brake which were provided on the drive transmission path | route which takes out the driving force of this rotary electric machine. It is a graph represented by the relationship between the deceleration state implement | achieved by the application example, a transient state, and a direct connection state.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Rotor 2 Rotor shaft 3 Rotor facing surface 4 Air gap 5 Rotor core 6 Rotor base 7 Steel plate 8 Reinforcing member 13 Piston 14 Liquid chamber of piston mechanism 48 Projection for fastening friction clutch 49 Stator 52 Output shaft 53 Friction clutch 55 Friction brake

Claims (9)

An axial gap type rotating electrical machine in which the stator and the rotor are arranged to face each other in the axial direction, and the variable air gap type rotating electrical machine in which the facing surfaces facing each other are movable in the axial direction.
A variable air gap type rotating electrical machine characterized in that, among the members having the facing surfaces, the axial movement amount of the outer diameter side portion and the axial movement amount of the inner diameter side portion are different. In the variable air gap type rotating electrical machine according to claim 1,
Of the rotor core of the rotor that is a member constituting the opposed surface, the rotor core outer diameter side portion is attached to the rotor base of the rotor so as not to be axially movable, and the rotor core inner diameter side portion is attached to the rotor base so as to be axially movable. A variable air gap rotating electrical machine. In the variable air gap type rotating electrical machine according to claim 1,
Of the rotor core of the rotor that is a member constituting the opposed surface, the rotor core inner diameter side portion is attached to the rotor base of the rotor so as not to be axially movable, and the rotor core outer diameter side portion is attached to the rotor base so as to be axially movable. A variable air gap rotating electrical machine. In the variable air gap type rotating electrical machine according to claim 1,
Of the rotor core of the rotor that is a member constituting the opposed surface, the rotor core inner diameter side portion is attached to the rotor shaft of the rotor so as not to be axially movable, the rotor core outer diameter side portion is attached to the rotor base of the rotor, and the rotor base is A variable air gap type rotating electric machine characterized by being attached to a rotor shaft so as to be axially movable. In the variable air gap type rotating electrical machine according to claim 4,
A variable air gap type rotating electric machine characterized in that at least one of a clutch and a brake is provided on a drive transmission path of the rotor, and the clutch or the brake is engaged and released by using the axial movement of the rotor base. . In the variable air gap type rotating electrical machine according to any one of claims 2 to 5,
The rotor core is obtained by laminating steel plates in the radial direction, and includes a permanent magnet. In the variable air gap type rotating electrical machine according to claim 6,
A hole extending in the radial direction is provided in the rotor core made of the steel plate, the reinforcing member is passed through the hole, and one of the inner diameter side end portion and the outer diameter side end portion of the reinforcing member is axially formed on the rotor base. A variable air gap type rotating electrical machine characterized in that it is mounted so as not to move and the other is mounted on a rotor base so as to be movable in the axial direction. In the variable air gap type rotating electrical machine according to claim 6,
Of the surfaces where the steel plate on the outer diameter side and the steel plate on the inner diameter side are in contact with each other, a concave portion is provided on one surface, a convex portion is provided on the other surface, and these concave and convex portions are engaged with each other, The variable air gap type rotating electrical machine is characterized in that the uneven portion defines axial movement of adjacent steel plates within a predetermined range. In the variable air gap type rotating electrical machine according to claim 8,
A hole extending in the radial direction is provided in the rotor core made of the steel plate, and the hole penetrates a hollow member made of an elastic material,
A piston mechanism that moves in the axial direction is provided between the rotor core outer diameter side portion and the rotor base, and the piston mechanism and the radially outer end of the hollow member are connected,
A variable air gap type rotating electrical machine characterized in that a hydraulic fluid is transferred to the piston mechanism via a hollow member so that an outer diameter side portion of the rotor core can be moved in an axial direction with respect to the rotor base.

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