JPH03219126A - motor braking device - Google Patents

Abstract

PURPOSE:To avoid the damage of a brake mechanism and to improve the controlability of a motor by providing a braking force giving mechanism for elastically moving a fixed disc to pushingly bring it into contact with a movable disc, and providing a braking face in the area of an elastic displacement due to the above pushingly contacting force of the movable disc. CONSTITUTION:A braking force giving mechanism (piston) 12 functions to elastically move a fixed disc 8 toward a movable disc 5 for pushingly bring it into contact with the movable disc 5. The movable disc 5 is elastically moved by the above pushingly contacting action to come into contact with a braking face 7b. The movable disc 5 is thereby held between the braking face 7b and the fixed disc 8 to brake a rotor 4. When the mechanism 12 is released from its function, both the movable disc 5 and the fixed disc 8 return elastically to their initial positions, and the disc 5 separates from the braking face 7b and the disc 8. Thus unnecessary rotary contact does not occur in the nonbraking state of a motor.

Description

[Detailed description of the invention] [Industrial application field] The present invention relates to a brake device for a motor.

[Prior art] As a motor equipped with a brake device, for example,
There is one disclosed in Japanese Patent No. -67053. In this conventional device, an annular piston comes into contact with a flange attached to the output shaft side, and this flange is sandwiched between the jaw on the fixed part side and the piston due to the pressing action of the piston, and brakes the rotation of the output shaft side. can be hung.

[Problems to be Solved by the Invention] However, the flange is connected to the output shaft via the index tape pull and the diaphragm, and the distance between the flange and the jaw is maintained by the elastic action of the diaphragm. Therefore, during braking, the index table moves in the direction of the output shaft, but a motor with such a configuration is difficult to apply to a device in which the index table indexes and rotates within the same plane. Moreover, since the flange and the piston are constantly in contact with each other due to the elastic action of the diaphragm, there is a drawback that the contact portion between the two is worn out by rotation of the flange.

SUMMARY OF THE INVENTION An object of the present invention is to provide a motor braking device that can eliminate the above-mentioned drawbacks.

[Means for Solving the Problems] To achieve this, in the present invention, a movable disk having elasticity is fixed to the rotor side, and a fixed disk having elasticity is arranged to be spaced apart from and facing the movable disk on the fixed part side. A braking force applying mechanism is provided on the fixed part side to elastically displace the fixed disk and press it against the movable disk, and a braking surface is provided in the area where the movable disk is elastically displaced due to this pressing action, thereby forming a brake device. did.

[Operation] By the operation of the braking force applying mechanism, the fixed disk is elastically displaced toward the movable disk and pressed against the movable disk.

The movable disk is also elastically displaced by this pressing action, and the movable disk comes into contact with the braking surface. As a result, the movable disk is sandwiched between the braking surface and the fixed disk, and braking is applied to the rotor. When the operation of the braking force applying mechanism is released, both the movable disk and the fixed disk elastically return, and the movable disk and the braking surface are separated, and the fixed disk and the movable disk are also separated. Therefore, unnecessary rotational contact does not occur during non-braking.

[Example] Hereinafter, an example embodying the present invention will be described based on the drawings.

1 is a case, and an output shaft 2 is rotatably housed and supported in the case 1, and an index table 3 is attached to the exposed end of the output shaft 2. A rotor 4 is fixedly fastened to the output shaft 2, and the rotation of the rotor 4 is directly transmitted to the output shaft 2. An elastic annular movable disk 5 is fastened to the rotor 4 by a plurality of screws 6. As shown in FIG. 2, the movable disk 5 has screw insertion holes 5a for the screws 6 arranged at equal intervals in the circumferential direction, and slits 5b are cut from the outer periphery to reach the screw insertion holes 5a. There is.

A flange 1a is provided on the inner periphery of the case 1, and a female threaded portion 1b is provided on the inner periphery of the flange 1a, and an annular clamp base 7 is screwed onto the female threaded portion 1b. The flange 1a has a plurality of screw holes IC arranged at equal intervals in the circumferential direction, and the clamp base 7 has a plurality of screw insertion holes 7a arranged at equal intervals in the circumferential direction at the same pitch as the screw holes 1c. . Following the clamp base 7, an elastic annular fixed disk 8 and a presser ring 9 are fitted into the case l. As shown in FIG. 2, a plurality of screw insertion holes 8a are arranged in the circumferential direction on the fixed disk 8 at the same pitch as the screw holes 1c, and the slits 8b are cut so as to reach the screw insertion holes 8a from the inner peripheral edge. has been done. The retainer ring 9 has a plurality of screw insertion holes 9a.
are arranged in the circumferential direction at the same pitch as the screw insertion holes 8a, and the screws 10 are inserted through the screw insertion holes 9a, 8a, and 7a and screwed into the screw holes 1c. Therefore, by tightening the screw IO, the clamp base 7 is fixed to the case 1 and the fixed disk 8 is fixed to the clamp base 7.

The inner diameter of the clamp base 7 is smaller than the outer diameter of the movable disk 5, and the inner diameter of the fixed disk 8 matches the inner diameter of the clamp disk 7. Also, a gap Co is provided between the fixed disk 8 and the end surface 7b of the clamp base 7, and the screwing position of the clamp base 7 with respect to the flange 1a is determined by the clearance between the end surface 7b of the clamp base 7 and the movable disk 5. As C1 occurs, the fixed disk 8
The setting is such that a clearance C2 is also generated between the movable disk 5 and the movable disk 5. That is, the thickness of the movable disk 5 is d
The following relational expression is set.

Co ""C+ +C2+d Furthermore, the radial area of the slit h5b of the movable disk 5 and the radial area of the slit 8b of the fixed disk 8 are the outer diameter side of the slit 5b and the inner diameter of the slit 8b when viewed from the direction of the output shaft 2. Polymerizes with the side.

A cover 11 is fitted and fixed to the open end of the case 1, and an annular cylinder chamber 11a is recessed in the inner end surface of the cover 11. An annular piston 1 is provided in the cylinder chamber 11a.
2 is accommodated so as to be slidable in the direction of the output shaft 2, and the distal end surface 12a of the piston 12 can come into contact with the fixed disk 8. The inner diameter of the tip surface 12a corresponds to the inner diameter of the fixed disk 8, and the outer diameter of the tip surface 12a is within the radial area of the slit 8b.

As shown in Fig. 3, there is an electromagnetic three-way valve 13 on the side of the case 1.
is installed, and its input port, output port, and exhaust port (all paths shown) are connected to the passage f in case 1.
! 1. n2+ β3 is connected. The passage βl is connected to a pressure air supply source (not shown), and the passages (!2.(!3) are connected to the cylinder chamber 11a,
Pressure air is supplied to and exhausted from the cylinder chamber 11a by controlling the opening and closing of the electromagnetic three-way valve 13.

When pressurized air is supplied to the cylinder chamber 11a, the piston 1
2 moves toward the movable disk 5 side, and urges the inner peripheral side of the fixed disk 8 toward the movable disk 5 side.

As a result, the inner circumferential side of the fixed disk 8 is elastically displaced toward the movable disk 5 so as to expand in diameter, and is pressed against the inner circumferential side of the movable disk 5. Furthermore, the elastic displacement of the fixed disk 8 presses the outer peripheral side of the movable disk 5 against the end surface 7b of the clamp base 7. As a result, as shown in FIG. 4, the outer peripheral side of the movable disk 5 is held in pressure contact between the fixed disk 8 and the end surface 7b of the clamp base 7, and the rotation of the rotor 4 is braked.

That is, the piston 12 constitutes a braking force applying mechanism, and the end surface 7
b becomes a braking surface for the movable disk 5.

The braking surface 7b must be set within the elastic displacement region of the movable disk 5, so that braking torque for the movable disk 5 can be obtained from both sides of the movable disk 5.

When pressurized air is exhausted from the cylinder chamber 11a, both disks 5 and 8 are elastically restored, and the piston 12 is returned to its initial position.

According to the brake device of this embodiment, the output shaft 2 does not displace in its axial direction during braking, and the index table 3 always indexes and rotates within the same plane. Therefore, the motor of this embodiment can be used without problems in an indexing device in which the index table indexes and rotates within the same plane. Also, when not braking, the fixed disc 8 and the movable disc 5
There are clearances CI and C2 between the movable disk 5 and the braking surface 7b, respectively, and rotational contact resistance due to the rotation of the rotor 4 does not occur anywhere other than the bearing. Therefore, smooth and highly accurate rotation control of the motor can be performed. Moreover, since the fixed disk 8 is interposed between the piston 12 and the movable disk 5, the external load torque from the output shaft 2 will not be transmitted to the piston 12, and the piston 12 will not rotate. There isn't. Therefore, the seal ring 14 fitted to the piston 12 is not damaged, and the sealing performance of the cylinder chamber 11a is maintained well.

Furthermore, in this embodiment, since the screwing position of the clamp base 7 with respect to the case 1 can be adjusted, if the interval C8 is set appropriately, the clearance CI can be adjusted by adjusting the screwing position of the clamp base 7 with respect to the case l. , C2 can be created. Therefore, the clearances CI and C2 can be easily set without increasing the accuracy of dimensional processing and assembly of each member.

Also, a slit 8b is formed in the fixed disk 8 and the movable disk 5.
, 5b, the elastic deformation of the disc 5.8 is performed smoothly, resulting in good braking.

Of course, the present invention is not limited to the above-mentioned embodiments. For example, the fixed disk and the movable disk may be laminated with thin plates, or both disks may be shaped like disc springs, thereby allowing elastic deformation of the disk. is performed more easily.

It is also possible to install the fixed disk so as to be inclined with respect to the output shaft, and by doing so, the return action of the fixed disk to the piston is performed more effectively, and the settings of the clearances C1 and C2 are further improved. It becomes easier.

[Effects of the Invention] As detailed above, the present invention fixes an elastic movable disk to the rotor side, and arranges an elastic fixed disk on the fixed part side so as to face the movable disk at a distance. A braking force applying mechanism is provided on the fixed part side to elastically displace the fixed disk and press it against the movable disk, and a braking surface is provided in the elastic displacement area of the movable disk due to this pressing action, so that the output shaft is not affected during braking. There is no axial displacement, contact resistance when not braking is eliminated, transmission of external load torque to the braking force applying mechanism is avoided, damage to the braking force applying mechanism is avoided, good motor control is achieved, and motor control is achieved within the same plane. This has an excellent effect in that it can be applied to an indexing device that rotates for indexing.

Furthermore, during braking, the movable disk is strongly pressed against both the braking surface and the fixed disk, so no force is generated to rotate the output shaft, and positional accuracy due to motor control can be compensated.

[Brief explanation of drawings]

The drawings show an embodiment of the present invention; FIG. 1 is a side sectional view when braking is not applied, FIG. 2 is an exploded perspective view of the main part, and FIG. 3 is a side sectional view of the main part of the braking force applying mechanism. , FIG. 4 is a side sectional view of the main part during braking. Rotor 4, movable disc 5, braking surface 7b, fixed disc 8, piston 12° constituting the braking force applying mechanism

Claims (1)

[Claims] 1 An elastic movable disk (5) is mounted on the rotor (4) side.
), and an elastic fixed disk (8) is arranged on the fixed part (7) side so as to face the movable disk at a distance, and a fixed disk (8) is arranged on the fixed part (11) side. A braking force imparting mechanism (12) that elastically displaces and presses against the movable disk (5) is provided, and a braking surface (7b) is provided in the elastic displacement region of the movable disk (5) due to this pressing action. Brake device for motor.