JP2017046547A - motor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a motor that achieves braking control for swinging in a radial direction of the motor.SOLUTION: The motor has a ball bearing 14 arranged at a base end part side of a case member 11, and comprises a coil spring 15 which supports a rotating shaft 21 movably in a shaft direction relative to the case member 11 and energizes a rotor 20 toward a tip side of the rotating shaft 21. In the rotor 20 are formed storage holes 22a1 and 22b1 which are pierced over a surface at the base end part side to an output side, of the rotor 20 and opened around the rotating shaft 21. The coil spring 15 is stored in the storage holes 22a1 and 22b1, and arranged so as to be interposed between end faces at the base end part sides of the storage holes 22a1 and 22b1 and an energizing member contacting end face, an end face at the output side of an inner ring of the ball bearing 14. In the coil spring 15, at least one end part of a spring base end-side end part and a spring output-side end part is inclined to form a sharp angle with respect to the shaft direction.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a motor, and more particularly to a motor provided with a mechanism that urges a rotor to a front end side of the rotating shaft while supporting the rotating shaft so as to be movable in the axial direction with respect to a case member.

In general, various types of mechanisms are installed in modern automobiles in order to provide a comfortable interior space and efficient driving.
A motor is often used as a drive source for these mechanisms, and various types of motors have been proposed according to the characteristics of the mechanism to be driven.
As one of such motors, for example, there is a pump motor used in ABS (anti-lock brake system) or the like.
The pump motor converts the rotational force into a linear reciprocating motion of the piston of the hydraulic pump, and the braking force of the brake disc is controlled by controlling the hydraulic pressure by the control device (for example, , See Patent Document 1).

Patent Document 1 discloses a motor device that can convert a motor rotational force into a linear reciprocating motion of a plunger (piston).
In this type of motor, the rotary shaft is supported so as to be movable in the axial direction relative to the yoke housing, and the armature core (rotor) is configured to be urged in the axial direction by a disc spring. .
That is, the disc spring is disposed so as to be interposed between the bottom portion (the bottom portion on the counter-output side) of the yoke formed in a cup shape and the counter-output side surface of the counter-output side bearing. As a result, the armature core (rotor) is pressed toward the distal end side (output side) in the axial direction via the non-output side bearing.

JP 2006-115612 A

As described above, in the technique such as Patent Document 1, since the rotor can be pressed toward the tip end side (output side) in the axial direction, a preload in the same direction can be applied to the rotor by the disc spring.
In addition, as an urging member for applying preload, not only the above-described disc spring but also a structure using a coil spring or the like has been proposed.
For example, the coil spring is mounted so that the rotating shaft passes therethrough, and the output side surface of the non-output side bearing and a step portion formed in the armature core (the inner wall portion of the insertion hole of the rotating shaft) It arrange | positions so that it bridge | crosslinks in the state (namely, the state shrunk | reduced rather than the natural length) in which urging | biasing force acts. By being arranged in this way, the coil spring can obtain a biasing force in the thrust direction and press the armature core in the output direction.
However, according to the configuration using a disc spring or a coil spring as in the prior art, it is possible to apply a preload in the thrust direction, but the armature is loaded from the radial direction as well. It is not possible to effectively deal with a motor that receives it.
That is, a preload can be applied in the thrust direction, but since the preload is not applied in the radial direction, it is not possible to effectively brake the vibration in the radial direction.
For this reason, there has been a problem that abnormal noise of the motor may occur due to the influence of the shake in the radial direction.

  An object of the present invention is to solve the above-described problems, and to provide a motor that realizes braking of vibration of the motor in the radial direction with a simple configuration.

  In the motor according to the present invention, the rotor is rotatably accommodated in the case member, and the output portion at the front end of the rotating shaft that passes through the rotor in the axial direction passes through the insertion hole of the case member. A motor projecting to the outside, and a ball bearing supporting the rotating shaft is disposed on the base end side of the case member, and supports the rotating shaft so as to be movable in the axial direction with respect to the case member. A coil spring that urges the rotor toward the distal end side of the rotary shaft, and the rotor is perforated from a surface on the proximal end side of the rotor to the output side and opens around the rotary shaft The coil spring is housed in the housing hole, and between the base end side end surface of the housing hole and the biasing member contact end surface that is the output side end surface of the inner ring of the ball bearing. Arranged to intervene In the coil spring, at least one of a spring proximal end that is an end contacting the proximal end side end surface and a spring output side end contacting the biasing member contact end surface This is solved by being inclined so as to form an acute angle with respect to the axial direction.

As described above, at least one end of the spring base side end (which is a seating surface) and the spring output side end (which is a seating surface) which are both ends of the coil spring according to the present invention is Inclined to form an acute angle with respect to the axial direction.
Specifically, the end portion of at least one of the spring base end portion and the spring output end portion is folded back in the direction of the other end portion, so that the radial direction (appended) (A force member contact end face, base end side end face) can be inclined to form an acute angle θ. That is, one end of the spring base end and the spring output end is inclined so as to form an acute angle (90 ° −θ) with respect to the axial direction (thrust direction).
In the known coil spring, both end portions are orthogonal bearing surfaces with respect to the axial direction (thrust direction). For this reason, they are disposed between the biasing member contact end surface and the base end side end surface (natural When the urging force is applied, the urging force is along the axial direction (thrust direction). For this reason, the urging force component force in the radial direction is substantially zero.
However, in the present invention, at least one of the spring base end (the seat surface) and the spring output end (the seat) is inclined with respect to the axial direction. Therefore, when the coil spring is disposed between the biasing member contact end surface and the base end side end surface and the biasing force is applied, the biasing force is inclined with respect to the axial direction (thrust direction). Therefore, a component component in the radial direction is generated.
Therefore, the radial shake of the rotor can be suppressed. That is, the rotor rotates so as to revolve in the circumferential direction and does not shake during rotation. Therefore, vibration can be suppressed and abnormal noise accompanying the vibration can also be effectively suppressed.

  At this time, as a specific application configuration, the output portion which is the output side end portion of the rotating shaft includes a coaxial portion coaxial with the rotating shaft, and an axis of the rotating shaft from the output side end portion of the coaxial portion. An eccentric portion extending along a direction, and the eccentric portion has an axis center different from the axis center of the rotating shaft and projects parallel to the axis of the rotating shaft In the state where the coil spring is provided with a biasing force interposed between the base end portion side end surface and the biasing member contact end surface, the eccentric portion is formed by the biasing force. It is preferable that at least one of the spring base end and the spring output end is inclined so as to form an acute angle with respect to the axial direction so as to face the direction. is there.

With such a configuration, it is possible to apply a strong urging force to the side with a larger weight, so that the rotation of the rotor is more stable and the deflection in the radial direction is further effectively suppressed.
Therefore, generation | occurrence | production of unusual noise can be suppressed more effectively.

Furthermore, both the spring proximal end and the spring output end are inclined so as to form an acute angle with respect to the axial direction, and the distal end of the spring proximal end is By being bent so as to be arranged in the output direction, the end portion on the spring base end side is inclined with respect to the axial direction, and the tip end of the spring output side end portion is bent so as to be arranged on the base end portion side. Accordingly, it is preferable that the end portion on the spring output side is inclined with respect to the axial direction.
Thus, since both sides are inclined, the urging force component force in the radial direction can be more effectively ensured, so that the vibration of the rotor in the radial direction can be more effectively suppressed.

Furthermore, the motor according to the present invention can be suitably used as a pump motor that is connected to a pump unit having a piston that changes oil pressure and operates the piston.
Furthermore, the motor according to the present invention can be suitably used as a pump motor for driving an antilock brake system.

According to the present invention, at least one of the spring base side end portion (which is a seating surface) and the spring output side end portion (which is a seating surface) of the coil spring is arranged with respect to the axial direction. The structure is inclined so as to form an acute angle.
For this reason, when the coil spring is disposed between the biasing member contact end surface and the base end side end surface and a biasing force is applied, the biasing force is not aligned with the axial direction, and thus is inclined. An urging force component component in the direction is generated.
Therefore, the vibration in the radial direction is suppressed, and thus the rotor can rotate stably. Thus, it is possible to effectively suppress the generation of abnormal noise due to the driving of the motor.
Specifically, the configuration is such that at least one of the spring base end and the spring output end is folded back (up) at the tip of at least one end. This is a configuration that can be easily realized. For this reason, a complicated structure and additional modification are unnecessary, and the vibration of the motor in the radial direction can be braked with a simple structure.

It is a schematic block diagram of the motor apparatus for pumps concerning one Embodiment of this invention. It is explanatory drawing which shows the structure of the coil spring which concerns on one Embodiment of this invention. It is comparative explanatory drawing which shows the direction of the urging | biasing force of the coil spring which concerns on one Embodiment of this invention. It is explanatory drawing which shows the direction of the urging | biasing force at the time of mounting the coil spring which concerns on one Embodiment of this invention. It is explanatory drawing which shows the structure of the coil spring which concerns on a modification. It is explanatory drawing which shows the direction of the urging | biasing force of the coil spring which concerns on a modification.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
Note that the configuration described below does not limit the present invention and can be variously modified within the scope of the gist of the present invention.
The present embodiment relates to a pump motor device that improves a coil spring that urges a rotor (armature) to an axial output side, and can effectively suppress the vibration of the rotor (armature) in the radial direction. It is.

1 to 4 show an embodiment of the present invention, FIG. 1 is a schematic configuration diagram of a pump motor, FIG. 2 is an explanatory diagram showing a structure of a coil spring, and FIG. 3 is an urging force of the coil spring. FIG. 4 is an explanatory view showing the direction of the urging force when the coil spring is mounted.
5 and 6 show modified examples of the above embodiment.

First, an example of the configuration of the pump motor device S according to the present embodiment will be briefly described.
The pump motor device S is a device that is preferably applied to the antilock braking system, and is configured by combining the motor unit 1 and the pump unit 2.

<About the motor unit>
The motor 10 constituting the motor unit 1 is a direct current motor, which is a so-called pump motor.
As shown in FIG. 1, the motor 10 is surrounded by a bottomed cylindrical yoke housing 11 (corresponding to a “case member”), and an opening (disposed on the output side) of the yoke housing 11. Has a basic configuration blocked by the end frame 12.
A field magnet 13 is fixed to the inner peripheral surface of the cylindrical portion of the yoke housing 11.
In the present embodiment, the magnet 13 has six magnetic poles. A bearing holding part 11a is formed in the bottom central part of the yoke housing 11 so as to project inward in a cylindrical shape. A ball bearing 14 is press-fitted into the inner peripheral surface of the bearing holding part 11a. A rotor 20 is rotatably accommodated inside the magnet 13, and a base end portion of a rotating shaft 21 of the rotor 20 is supported by a ball bearing 14.

  The rotor 20 includes a rotating shaft 21, a rotor core 22 assembled to the rotating shaft 21 so as to be integrally rotatable, a coil 23 wound around the rotor core 22, and fixed to the rotating shaft 21 and electrically connected to the coil 23. And a commutator 24.

  As shown in FIG. 1, the rotor core 22 is composed of four parts in the axial direction. In this case, the first core block A, the second core block B, the third core block C, and the fourth core block D are sequentially arranged from the base end side (the ball bearing 14 side) of the motor 10. The first to fourth core blocks A to D are provided with 18 tooth portions 22x for winding the coil 23 at equal intervals in the circumferential direction on the outer peripheral side. That is, in this embodiment, the number of salient poles on the rotor 20 side is set to “18” with respect to the number of magnetic poles “6” of the magnet 13. Each teeth part 22x is comprised by the 1st-4th core block AD and the same shape.

  On the inner peripheral side of the rotor core 22, the base ends of the tooth portions 22 x are connected to each other in an annular shape, but the first and fourth core blocks A and D, the second core block B, and the third core block C are connected. And the annular shape of the core sheet constituting each block is different. In this embodiment, the outer diameter of the annular shape of the core sheet which comprises each block is made the same, and the internal diameter is varied.

  As for the 3rd core block C, the hole of the inner peripheral side serves as a shaft hole 22c1 for press-fitting of the rotating shaft 21, and the third core block C is formed by press-fitting the rotating shaft 21 into the shaft hole 22c1. It is fixed to the rotating shaft 21. The first core block A is fixed to the second core block B, the second core block B is fixed to one side of the third core block C, and the fourth core block D is fixed to the third core block C. It is fixed to the other side. That is, the first, second, and fourth core blocks A, B, and D are not directly fixed to the rotating shaft 21 but are indirectly fixed to the rotating shaft 21 through the third core block C. The third core block C is configured by laminating a plurality of core sheets made of magnetic metal plates in the axial direction.

  The second core block B has an accommodation hole 22b1 in which the inner diameter of the inner peripheral hole is slightly larger than the inner diameter of the shaft hole 22c1 of the third core block C. The accommodation hole 22b1 of the second core block B is It is used for accommodating the coil spring 15 that is externally supported by the rotary shaft 21. The second core block B is configured by laminating a plurality of core sheets made of a magnetic metal plate in the axial direction.

The first and fourth core blocks A and D have the same shape including the tooth portion 22x. The inner and outer holes of the first and fourth core blocks A and D are accommodation holes 22a1 and 22d1 whose inner diameter is larger than the inner diameter of the second core block B (see FIG. 1). The housing hole 22a1 of the one core block A is used for housing a part of the coil spring 15 and the bearing holding portion 11a (ball bearing 14), and the output side housing hole 22d1 of the fourth core block D is a part of the commutator 24. Used for containment. Each of the first and fourth core blocks A and D is configured by laminating a plurality of core sheets made of magnetic metal plates in the axial direction.
The core sheets of the first to fourth core blocks A to D are connected to each other before and after being laminated in the axial direction by caulking fixing portions that are appropriately provided in the annular portion, and are configured as one rotor core 22. .

  The rotor core 22 composed of the first to fourth core blocks A to D is inserted into the shaft hole 22c1 of the third core block C, so that the third core block C with respect to the rotation shaft 21 is inserted. Is directly fixed, and the first, second, and fourth core blocks A, B, and D are indirectly fixed. The base end portion of the rotating shaft 21 is rotatably supported by the ball bearing 14, and the outer ring of the ball bearing 14 is press-fitted into the bearing holding portion 11a of the yoke housing 11, whereas the rotating shaft 21 is loosely fitted to the inner ring. Has been. That is, the rotating shaft 21 (the rotor 20) is supported so as to be movable in the axial direction. A part of the tip end portion (arranged on the output side) of the bearing holding portion 11 a that holds the ball bearing 14 is inserted into and accommodated in the accommodation hole 22 a 1 of the first core block A.

Also, the inner ring of the ball bearing 14 (the output side end surface of the inner ring is the “biasing member contact end surface”) and the surface on the base end side of the surface facing the axial direction of the third core block C (the surface concerned) Is indicated as “base end side end face 22e”), and the coil spring 15 is stretched between them. The coil spring 15 is externally supported by the rotating shaft 21 and is accommodated in the accommodating holes 22a1 and 22b1 of the first and second core blocks A and B. The coil spring 15 is formed with an orthogonal seating surface portion orthogonal to the axial direction at the output side end portion in the axial direction, and the orthogonal seating surface portion is a base end side that is an end surface of the third core block C. It is in contact with the end face 22e.
The other end side of the coil spring 15 (base end side: opposite to the output side) is in contact with the axial output side end surface of the inner ring of the ball bearing 14, but the other side has an orthogonal seat portion. It is not formed and has a special shape.
Since the configuration of the other end of the coil spring 15 is the main configuration of the present invention, it will be described in detail later.
The coil spring 15 uses the inner ring of the ball bearing 14 as a fulcrum, and exerts its urging force on the end surface (base end side end surface 22e) of the third core block C to press the rotor 20 to the front end side. Give preload.

Further, as shown in FIG. 1, a commutator 24 is fixed to the distal end side of the rotating shaft 21. As shown in FIG. 1, a plurality of segments 24 a are fixed to the outer peripheral surface of the commutator 24, and the terminal wire of the coil 23 wound around the tooth portion 22 x of the rotor core 22 corresponds to the corresponding segment 24 a. Connected. A tip portion of the rotating shaft 21 protruding from the commutator 24 is an output portion 21a.
The output portion 21a includes a coaxial portion 121a that is coaxial with the rotating shaft 21, and an eccentric portion 121b that has an axis at a position shifted from the axis of the rotating shaft 21 (an eccentric position).
A front bearing 121c is disposed on the outer periphery of the coaxial portion 121a, and an output bearing 121d is disposed on the outer periphery of the eccentric portion 121b. In this example, a needle bearing is used as the output bearing 121d.
The front bearing 121 c is disposed in the pump housing 31 that constitutes the pump unit 2, and the outer peripheral portion of the output bearing 121 d is disposed so as to contact the piston 32 that constitutes the pump unit 2.

Further, as described above, the rotor 20 has 18 teeth portions 22x, and 18 segments 24a are arranged in the commutator 24 (18 slots and 18 segments). Moreover, in this embodiment, the magnet 13 arrange | positioned at the yoke housing 11 which is a stator is comprised so that it may become 6 magnetic poles.
In this embodiment, for example, the pressure equalization line is designed to be 120 ° connection.

The end frame 12 is attached to the opening of the yoke housing 11 that houses the rotor 20 and the like configured as described above. From the insertion hole 12a provided in the center portion of the end frame 12, an output portion 21a provided at the tip of the rotating shaft 21 protrudes to the outside.
A brush device 25 is provided on the inner side surface of the end frame 12. The brush device 25 includes a rectangular cylindrical holder portion 26, and a rectangular parallelepiped brush 27 is accommodated so as to be able to advance and retract in the radial direction. The brush 27 receives the urging force of the spring 28 at its rear end surface, and comes into pressure contact with the segment 24 a on the outer peripheral surface of the commutator 24. Then, power is supplied to the coil 23 of the rotor 20 through the brush 27 and the commutator 24, and a magnetic field for rotation is generated in the rotor 20.

  Further, an end frame holding portion 12b is integrally formed in the vicinity of the insertion hole 12a formed in the end frame 12 so as to protrude from the output side surface of the end frame 12 to the axial output side. Embedded in the end frame holding portion 12b is a wiring / use plate 12c having one end electrically connected to the brush 27. The end frame holding part 12 b is fixed to the pump housing 31.

<About the pump unit>
Next, the pump unit 2 will be described.
As shown in FIG. 1, the pump unit 2 includes a pump housing 31, and a transmission chamber 31 a for storing an eccentric portion 121 b protruding from the motor unit 1 and an output bearing 121 d on a surface facing the motor unit 1. Is formed. The transmission chamber 31a is a hole bored so as to be recessed in a cylindrical shape with a bottom along the axial direction of the rotary shaft 21 in the pump housing 31, and the output bearing 121d. A space size is ensured so that the eccentric part 121b which is provided with the exterior can be eccentrically moved.

  The pump housing 31 is formed with a piston accommodating portion 31b that extends radially outward from the transmission chamber 31a. The piston 32 housed in the piston housing part 31b is in contact with the output bearing 121d in the radial direction of the eccentric part 121b, and slides in the piston housing part 31b as the rotor 20 rotates. As the piston 32 slides, the fluid (hydraulic oil) in the hydraulic chamber 31c communicating with the piston accommodating portion 31b is pressurized, and the fluid (hydraulic oil) filled in the hydraulic chamber 31c is pumped.

<Assembly of motor part and pump part>
The motor unit 1 configured as described above is assembled to the pump unit 2.
At this time, the end frame holding portion 12 b constituting the end frame 12 is fixed to the pump housing 31.
In addition, the eccentric portion 121b on which the output bearing 121d is packaged is disposed inside the transmission chamber 31a. At this time, the outer wall of the output bearing 121 d is in contact with the end of the piston 32.
And the front bearing 121c is fixed so that the opening end by the side of the motor part 1 in the transmission chamber 31a may be obstruct | occluded. That is, it is fixed to the inner wall of the transmission chamber 31a (in this example, indirectly).
At this time, an annular collar K1 is attached to the outer peripheral portion of the front bearing 121c.
That is, the outer diameter of the front bearing 121c with the collar K1 attached is the maximum diameter of the collar K1 itself, and this maximum diameter is configured to be equal to the opening diameter of the transmission chamber 31a.
Therefore, the difference between the opening diameter of the transmission chamber 31a and the diameter of the front bearing 121c itself can be compensated by the collar K1, and the front bearing 121c is fixed to the opening of the transmission chamber 31a via the collar K1. It becomes possible.
As described above, when the rotary shaft 21 is rotated by the rotation of the motor 10, the pump motor device S that is assembled and assembled causes the output bearing 121d attached to the eccentric portion 121b to perform an eccentric motion, and thus for output. The piston 32 pressed against the bearing 121d is reciprocated in the horizontal direction. The fluid is pumped by the movement of the piston 32.

The motor 10 according to the present embodiment is suitably used as a pump motor for performing hydraulic control of an antilock brake system mounted on a vehicle.
The anti-lock brake system is a mechanism that is connected to a hydraulic pipe that connects between a master cylinder and a brake caliper constituting the brake system, for example, and releases a wheel lock by braking.
This anti-lock brake system includes, for example, an ABS actuator, a control device, a sensor, and the like, and the brake fluid (hydraulic fluid) in the brake dial of the locked wheel is mastered by the pump motor in the ABS actuator. It is pumped back to the cylinder, and the lock is released by lowering the hydraulic pressure.
The wheel lock is monitored by a sensor (rotational speed sensor or the like), and a series of operations is controlled by a control device (for example, a control unit) that receives a signal from the sensor.
The motor 10 according to the present embodiment is suitably used as a pump motor for this antilock brake system.

<About structure and function of coil spring>
Next, details of the structure and function of the coil spring 15 according to the present embodiment will be described with reference to FIGS.
As shown in FIG. 2, the basic structure of the coil spring 15 according to the present embodiment is a general helical spring.
However, the coil spring 15 according to the present embodiment is different in structure at one end from a general helical spring.
As described above, the coil spring 15 is formed with an orthogonal seating surface portion orthogonal to the axial direction at the axial output side end portion (hereinafter referred to as “spring output side end portion 15A”). The surface portion is in contact with the end face of the third core block C (the base end side end face 22e which is the base end side face among the faces facing in the axial direction).
The other end side of the coil spring 15 (base end side: opposite to the output side, hereinafter referred to as “spring base end side end 15B”) is configured as shown in FIG. That is, the spring proximal end 15B (seat surface portion) is not formed so as to be orthogonal to the axial direction, and is perpendicular to the axial direction (hereinafter also referred to as “thrust direction”). The tip portion thereof is folded back (bounced up) so as to be inclined by an angle θ1 with respect to “radial direction”. In other words, the tip portion is folded back so as to be inclined by an angle (90 ° −θ1) with respect to the thrust direction. Note that θ1 is an acute angle.
The spring output side end 15 </ b> A and the spring base end 15 </ b> B are so-called “seat surfaces” at both ends of the coil spring 15.

That is, as shown in FIG. 2, in the natural length state in which no urging force is generated, the spring proximal end 15B is against the output side surface of the ball bearing 14 (this surface is a surface along the radial direction). Thus, the tip portion is folded back so that the angle θ1 is inclined.
In this state, when the spring output side end portion 15A is brought into contact with the base end side end surface 22e of the third core block C to apply a biasing force to the coil spring 15 (that is, when the coil spring 15 is contracted), FIG. As shown in FIG. 3B, an urging force F2 inclined by an angle θ1 with respect to the thrust direction can be obtained.

This will be described in detail with reference to FIG.
As shown in FIG. 3A, in the normal coil spring 15 ′, orthogonal seating surface portions orthogonal to the axial direction are formed on both the output side end portion and the opposite end portion in the thrust direction.
Therefore, when an urging force is applied (that is, when the coil spring 15 'is contracted), all components of the urging force F1 are directed in the thrust direction (radial direction component force ≈ 0).
On the other hand, when the spring proximal end 15B is bent so as to form an angle θ1 with respect to the radial direction as in the present embodiment, if a biasing force is applied (that is, the coil spring 15 is contracted). 3) As shown in FIG. 3B, it is possible to obtain an urging force F2 inclined by an angle θ1 with respect to the thrust direction.
That is, the magnitude of the urging force F2 itself is determined by the relationship between the spring constant and the difference with respect to the natural length, and thus is almost the same as the urging force F1, but the direction of addition is changed.
Therefore, in the radial direction, it is possible to obtain a biasing force (component force) of radial biasing force Fr1 = F2 × sin θ1.
Therefore, the radial urging force Fr1 can effectively suppress the vibration of the rotor 20 in the radial direction.

Further, as shown in FIG. 4, it is preferable that the direction of the urging force F2 is a high load direction.
In other words, it is preferable to set the biasing force F2 so that the eccentric portion 121b is formed and the weight increases.
In other words, in the natural length state, if the position that is farthest from the side where the weight is increased (the side where the eccentric portion 121b is formed) of the spring base end 15B is the fulcrum O1, the fulcrum O1 is It is preferable that the spring proximal end 15B bends so as to be inclined at an angle θ1 with respect to the output side surface of the ball bearing 14 while in contact with the output side surface of the ball bearing 14.
In addition, when the rotor 20 rotates in a state where the coil spring 15 is set between the output side surface of the ball bearing 14 and the base end portion side end surface 22e of the third core block C and given a biasing force, The coil spring 15 rotates with the inner ring of the ball bearing 14. For this reason, this urging force F2 is always directed to the side where the eccentric portion 121b is formed and the weight is increased.
Since it is configured in this way, even if it is a special mechanism having the eccentric portion 121b at the output-side tip portion of the rotating shaft 21, the biasing force F2 acts on the more stable side. It is possible to more effectively suppress the vibration in the radial direction.

In the present embodiment, the spring base end 15B is not an orthogonal seating surface, but is inclined at an angle θ1 with respect to the radial direction. However, the present invention is not limited to this, and the spring output end 15A is not limited thereto. This may be configured so that the angle θ1 is inclined with respect to the radial direction without using the orthogonal bearing surface.
In other words, either one of the spring proximal end 15B or the spring output end 15A may be configured to be inclined by the angle θ1.

<Modification example>
Next, modified examples will be described with reference to FIGS.
As shown in FIG. 5, the coil spring 15 according to the modified example has its distal end folded back so that the spring proximal end 15 </ b> B forms an angle θ <b> 1 with respect to the radial direction, as in the above embodiment. .
In this example, the end portion of the spring output side end portion 15A is also folded so as to form an angle θ1 with respect to the radial direction. That is, in this example, both ends of the coil spring 15 are folded back.
More specifically, as shown in FIG. 5, the fulcrum O2 of the spring output side end 15A at the angle θ1 is arranged on the thrust direction axis at the position corresponding to the fulcrum O1 of the angle θ1 of the spring base end 15B. It is comprised so that. The distal end side of the spring proximal end portion 15B is folded back toward the output side, and conversely, the spring output side end portion 15A has a proximal end side that is the opposite side (that is, the ball bearing 14 is The tip side is folded back toward the side where it is placed. Both of them are folded around the fulcrum O1 and the fulcrum O2 so as to form an angle θ1 with respect to the radial direction.

When the coil spring 15 configured in this way is set between the output side surface of the ball bearing 14 and the base end side end surface 22e of the third core block C and is given a biasing force, the magnitude of the biasing force F3 is large. Since it is determined by the relationship between the spring constant and the difference with respect to the natural length, it is almost the same as the urging forces F1 and F2, but the addition direction changes.
The urging force F3 is inclined so as to form an angle θ2 with respect to the thrust direction, but the angle θ2> the angle θ1.
For this reason, in the radial direction, it is possible to obtain an urging force (component force) of radial urging force Fr2 = F3 × sin θ2.
Since the angle θ2 is 0 ° <angle θ2 <90 °, the radial biasing force Fr2> the radial biasing force Fr1.
Therefore, the radial urging force Fr2, which is a radial urging force larger than the radial urging force Fr1, can more effectively suppress the vibration of the rotor 20 in the radial direction.

As described above, according to the above-described embodiment and the modified example, it is possible to perform simple processing on the end portions of the coil spring 15 (spring base end side end portion 15B, spring output side end portion 15A). Radial deflection can be suppressed.
That is, at the end of the coil spring 15, the direction in which the urging force is applied can be shifted from the thrust direction only by turning back the tip so as to form a predetermined angle with respect to the radial direction. You can get a component to.
Thus, according to the present embodiment, it is possible to suppress the vibration of the rotor 20 in the radial direction with a simple configuration, and thereby it is possible to effectively suppress the generation of abnormal noise.

S .... Pump motor device, 1 .... Motor part, 2 .... Pump part,
10. ・ Motor,
11..Yoke housing (case member), 11a..Bearing holding part,
12. End frame,
12a .. insertion hole, 12b .. end frame holding part, 12c .. wiring combined plate,
13. Magnets
14. Ball bearings,
15, 15 '· · coil spring,
15A ... Spring output side end, 15B ... Spring base end side,
20. Rotor,
21 .. Rotating shaft, 21a .. Output part, 121a .. Coaxial part, 121b .. Eccentric part,
121c ... Front bearing, 121d ... Output bearing,
22 .. Rotor core, 23 .. Coil,
22a1, 22b1, .. accommodation hole, 22c1, .. shaft hole, 22d1, .. output side accommodation hole,
22e .. Base end side end face,
22x · Teeth club,
A to D ··· first to fourth core blocks,
24 .. Commutator, 24a .. Segment,
25 .. Brush device, 26 .. Holder part, 27 .. Brush, 28 .. Spring,
31 .... Pump housing, 31a ... Transmission chamber, 31b ... Piston housing,
31c ... Hydraulic chamber, 32 ... Piston,
K1 color

Claims (5)

A rotor in which a rotor is rotatably accommodated in a case member, and an output portion at a distal end of a rotating shaft penetrating the rotor in an axial direction protrudes outside through an insertion hole of the case member;
A ball bearing that supports the rotating shaft is disposed on the base end side of the case member, supports the rotating shaft so as to be movable in the axial direction with respect to the case member, and supports the rotor at a tip end of the rotating shaft. It has a coil spring that biases to the side,
The rotor is formed with a receiving hole which is perforated from the surface on the base end side of the rotor to the output side and opens around the rotation axis,
The coil spring is housed in the housing hole and is disposed so as to be interposed between a base end side end surface of the housing hole and a biasing member contact end surface which is an output side end surface of the inner ring of the ball bearing. And
In the coil spring, at least one end portion of a spring base end portion which is an end portion in contact with the base end portion end surface and a spring output side end portion in contact with the biasing member contact end surface Is inclined to form an acute angle with respect to the axial direction. The output portion that is the output side end portion of the rotation shaft includes a coaxial portion that is coaxial with the rotation shaft, an eccentric portion that extends from the output side end portion of the coaxial portion along the axial direction of the rotation shaft, and Is configured with
The eccentric portion has an axis center different from the axis center of the rotating shaft, and protrudes in parallel with the axis of the rotating shaft,
The coil spring is interposed between the base end side end surface and the biasing member contact end surface and is provided with a biasing force.
At least one end of the spring base end and the spring output end is in the axial direction so that the biasing force is directed in the direction in which the eccentric portion is formed. The motor according to claim 1, wherein the motor is inclined so as to form an acute angle. Both the spring base side end and the spring output side end are inclined so as to form an acute angle with respect to the axial direction.
By bending the distal end of the spring proximal end to be disposed in the output direction, the spring proximal end is inclined with respect to the axial direction, and the distal end of the spring output end is The motor according to claim 2, wherein the spring output side end portion is inclined with respect to the axial direction by being bent so as to be disposed on the base end portion side.   The motor according to any one of claims 1 to 3, wherein the motor is a pump motor that is connected to a pump unit including a piston that changes oil pressure to operate the piston. The motor according to claim 4, wherein the motor is a pump motor for driving the antilock brake system.

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