JP5827282B2 - Braking structure - Google Patents

Description

  The present invention relates to a braking structure.

  Conventionally, in an industrial machine such as a motor or a speed reducer, a braking structure for applying a braking force to a rotating shaft protruding from a machine main body is provided on a rotating shaft M on a brake side as shown in FIG. A braking device 96 (see, for example, Patent Document 1 and Patent Document 2) that fixes the disk member 91 in an outer fitting shape and clamps and brakes the braked disk portion 91a of the rotating disk member 91 is provided as a motor casing or a speed reducer. It was fixed to a fixed other member 99 such as a main body.

JP-A-11-223231 JP 2004-44681 A

However, the rotating shaft M on the braked side extends due to heat, (in the case of a motor), the motor shaft (rotating shaft M) moves to a magnetically balanced position along with energization of the motor, The position of the rotation axis M may move due to the change, or the position of the rotation axis M may be displaced due to rattling of the machine itself. In such a case, the rotation shaft M causes expansion / contraction movement (expansion / contraction displacement) in the arrow N direction (axial center direction N) shown in FIG. 4, and the disk member 91 fixed to the rotation shaft M also moves in the arrow N direction. . However, since the braking device 96 is fixed to the fixed other member 99, the disc member 91 that has moved contacts one of the brake shoes 96a and 96b, and the brake shoes 96a and 96b are in a state of being released. There was a problem that dragging occurred.
Therefore, in order to solve the dragging problem of the brake shoes 96a and 96b, if the air gap dimension S is set larger than the dimension in which the disc member 91 is displaced in the axial direction N, the movement stroke of the brake shoe becomes larger and the operation becomes active. There is a problem that the sound becomes loud and a problem that the shock (vibration) becomes large. Particularly, when the braking device 96 is a spring-operated electromagnetic open type, the air gap dimension S is large, so the reference value of the movable core stroke is set. Although it is necessary to increase it, in this case, it is used in a region where the attractive force of the electromagnetic coil is weakened, and there is a problem that the spring force (shoe pressing force) becomes smaller for the size of the iron core.

  Therefore, the present invention solves the conventional problems as described above, and even if the braked rotating shaft is displaced in the axial direction, the brake shoe does not drag and the air gap size can be set small. An object of the present invention is to provide a braking structure that can be used in a region where the attractive force of the electromagnetic coil is large and has a large generated braking force.

In order to achieve the above object, the braking structure of the present invention includes a disk member fixed to the rotating shaft on the braked side in an outer fitting manner, and an outer periphery of the rotating shaft mounting boss portion of the disk member via a bearing member. A bracket member that is attached in a fitting manner and is rotatable about the axis of the rotation shaft relative to the disk member; and a braking device that is fixed to the bracket member and clamps the disk member to brake the disk member. A brake unit, and a fixing member attached to the other fixing member. The bracket member is slidably held along the axis between the bracket member and the fixing member. slides detent means for performing a stop is provided, the upper Symbol slide detent means includes a single guide shaft which is projecting from one of the bracket member and the fixing member, the bracket member and the solid And the guide receiving hole portion in which the guide shaft portion provided at the other above one of the members is inserted, consists of, the fixing member includes an adjuster bolt for multiple level adjusting, the guide shaft by the adjustment of the adjuster bolt The axial center of the part is arranged in parallel with the axial center of the rotating shaft.
The guide receiving hole is formed by an inner peripheral surface of the sliding bearing member by fitting a sliding bearing member for sliding into a through hole provided in the other of the bracket member and the fixing member.

  According to the present invention, when the disc member moves with the axial displacement of the rotating shaft, the braking device automatically moves with the same axial displacement. Therefore, the brake shoe is not dragged, and the air gap dimension can be set small. By reducing the size of the air gap, it can be used in a region where the attractive force of the electromagnetic coil is large, and the generated braking force can be increased. Furthermore, the operating sound and impact (vibration) of the shoe (pad) of the braking device can be reduced.

It is a principal part cross-section side view which shows one Embodiment of this invention. It is a front view. It is a cross-sectional side view of the principal part. It is a principal part cross-sectional side view for demonstrating a prior art.

Hereinafter, the present invention will be described in detail based on illustrated embodiments.
1 and 2, the braking structure according to the present invention is for braking the rotation of a rotating shaft M protruding from a machine body K of an industrial machine such as a motor or a speed reducer. A cylindrical wall-shaped rotating shaft mounting boss portion 11 that is fixed to the braked rotating shaft M in an outer fitting manner, and a braked disk portion (disk portion) 12 provided on the boss portion 11 in the shape of an outer casing. The disk member 1 and the boss portion 11 of the disk member 1 are attached to the outer periphery of the disk member 1 via bearing members 3 and 3 such as ball bearings. A bracket member 5 that is rotatable around La and is not slidable along the axis La of the rotation axis M with respect to the disk member 1, and a braked disk portion 12 of the disk member 1 that is fixed to the bracket member 5 by a connecting bolt 4. Brake unit Y provided with braking device 6 It has.

  The disk member 1 is integrated with the rotating shaft M by a key 21 interposed between the disk member 1 and the rotating shaft M. The boss portion 11 is sandwiched between the diameter-enlarged stepped portion Mb on the base end side of the rotation shaft M and the plate-like pressing member 22 attached to the distal end surface Ma of the rotation shaft M, and the rotation shaft M On the other hand, sliding movement along the rotation axis La (in the rotation axis direction N) is prevented.

The bracket member 5 includes a short cylindrical portion in which a central hole portion 52 is fitted through the bearing members 3 and 3, and a plate-like connecting portion 53 provided in the outer cylindrical shape in the short cylindrical portion. Have.
The connecting portion 53 is formed in an X shape when viewed from the front, and the braking device 6 is fixed to the cantilever shape by the connecting bolt 4.

  Further, the step portion provided on the outer peripheral surface (side) of the boss portion 11 of the disk member 1, the step portion provided on the inner peripheral surface (side) of the central hole portion 52 of the bracket member 5, and the bracket member 5 are fixed. The bracket member 5 and the bearing members 3 and 3 are attached to the disk member 1 by the outer ring pressing member 23 that presses the outer ring portion of the bearing member 3 and the inner ring pressing member 24 that is fixed to the disk member 1 and presses the inner ring portion of the bearing member 3. On the other hand, sliding along the rotational axis La is prevented.

And the fixing member 7 attached to other fixed members G, such as a base (base frame) of a machine main body K or a building, is provided.
The fixing member 7 includes a flat base portion 71, two (plurality) mounting bolts 72, 72 that pass through the base portion 71, and three (plurality) level adjustment screws that are screwed to the base portion 71. Adjuster bolts 73, 73, 73, and a lock nut 74 that is screwed onto the adjuster bolt 73 to fix the adjuster bolt 73 to the base portion 71 are provided.
The fixing member 7 is fixed by bringing the tip ends of the adjuster bolts 73, 73, 73 into contact with the other fixing member G and screwing the mounting bolts 72, 72 to the fixing other member G.

  Further, the bracket member 5 is slidably held between the bracket member 5 and the fixing member 7 in a direction parallel to the rotation axis La with respect to the fixing member 7 (fixed other member G), and the rotation axis La. A slide detent means 8 is provided to prevent rotation around.

  The slide detent means 8 includes a guide shaft portion 81 projecting from the fixing member 7 and a guide receiving hole portion 82 penetrating the connecting portion 53 of the bracket member 5. Lb (hereinafter also referred to as the guide shaft axis Lb) and the axis Lc of the guide receiving hole 82 (hereinafter also referred to as the guide receiving hole axis Lc) are parallel to the rotational axis La. Arrange.

The guide shaft portion 81 projects from a column portion 75 erected from the base portion 71 of the fixing member 7 in a direction orthogonal to the axis of the adjuster bolt 73 in a side view.
When the mounting surface Ga of the other fixed member G is not parallel to the rotation axis La, the guide shaft axis Lb can be arranged in parallel to the rotation axis La by adjusting the adjuster bolt 73.

  The guide receiving hole portion 82 includes a sliding bearing member 88 for sliding such as an oil-free bush in a through hole 51 provided in the connecting portion 53 (in parallel with the axis of the rotating shaft mounting hole 11a of the disk member 1). It is formed by fitting (by the inner peripheral surface of the sliding bearing member 88).

  The braking device 6 has a known structure, and the illustrated example is a spring-actuated (braking) electromagnetic release type, a disk-shaped fixed iron core 63 having a coil for an electromagnet, a disk-shaped movable iron core 65, And a holding member 62 having a plate-like mounting portion 62a disposed on the electromagnet portion 61 in a face-to-face manner (parallel to the end face of the movable iron core 65 in a side view) with a predetermined interval. A plurality of guide rods 64 for connecting and integrating the electromagnet portion 61 and the holding member 62, a reinforcing rod 70 for connecting and integrating the electromagnet portion 61 and the holding member 62, and the electromagnet portion 61 and the mounting portion 62a. A pair of brake shoes (pads) 66 and 67, a braking force receiving member 68, and a braking (actuating) spring 60 that constantly urges and urges the movable iron core 65 and the stationary iron core 63 in a separating direction. Yes.

Further, one brake pad 67 is attached so as to be interlocked with the movable iron core 65, and is disposed in a face-to-face manner on one flat surface (end surface) of the braked disk portion 12.
The other brake pad 66 is attached to the mounting portion 62a, and is disposed in a face-to-face manner on the other flat surface (end surface) of the braked disc portion 12. The other brake shoe 66 is attached to the attachment portion 62a via an adjustment screw 69.
The braking force receiving member 68 receives the tangent force of the pair of brake shoes 66 and 67 that reciprocate in the direction of approaching and separating from each other (force in the tangential direction of the braked disk portion 12 acting on the brake shoes 66 and 67). The pair of brake shoes 66 and 67 are enclosed, slidable in the direction of the brake pressing operation, and held stationary in the direction of the tangential force, and the guide rods 64 and 64 are relatively slid. It is movably inserted and fixed to the bracket member 5.
That is, the braking force receiving member 68 attaches the clamping unit U in which the electromagnet portion 61 and the holding member 62 are connected and integrated by the guide rod 64, the reinforcing rod 70, and the like so as to be capable of floating in a minute dimension.
Further, a spring member 59 that elastically biases the mounting portion 62a of the holding member 62 and the braking force receiving member 68 so as to be separated from each other, and a regulating member that prevents separation beyond a predetermined separation dimension Thus, the air gap dimension S can be adjusted in the brake released state by aiming the centering of the clamping unit U.

When the electromagnet part 61 is energized, the braking device 6 makes the movable iron core 65 and the fixed iron core 63 approach or contact each other by electromagnetic force, and the brake release 12 in which the braked disk part 12 and the brake shoes 66 and 67 are separated from each other is released. It becomes.
Further, when energization to the electromagnet portion 61 is stopped, the movable iron core 65 is separated from the fixed iron core 63 by the elastic force of the braking spring 60, and the pair of brake shoes 66, 67 are relatively close to each other, The pair of brake shoes 66 and 67 are configured to clamp and brake the outer peripheral edge portion 12a of the braked disc portion 12.

Next, the usage method (action) of the braking structure of the present invention will be described.
Before going to the construction site where the machine main body K is disposed in advance, the disk member 1, the bearing members 3 and 3, the bracket member 5 provided with the guide receiving hole 82, the braking device 6, and the outer ring pressing member 23 and the inner ring pressing member 24 are assembled to manufacture the brake unit Y. Further, the fixing member 7 provided with the guide shaft portion 81 and the pressing member 22 are manufactured.

Then, the brake unit Y, the fixing member 7 and the pressing member 22 are carried to the construction site, the disk member 1 is fitted on the rotating shaft M on the braked side, and the pressing member 22 is attached to the rotating shaft M. The brake unit Y is fixed to the rotating shaft M.
Next, the guide shaft portion 81 on the fixing member 7 side is inserted into the guide receiving hole portion 82 on the brake unit Y side, and the three adjuster bolts 73, 73, 73 are screwed back and forth, so that the guide shaft axis Lb is These are arranged so as to be parallel (shaped) to the rotation axis La. Thereafter, the mounting bolt 72 is screwed onto the other fixing member G, the fixing member 7 is fixed, and the construction is completed.

Then, the electromagnet 61 is energized to release the brake (open the shoe), and after confirming and adjusting the air gap dimension S, the rotating shaft M is rotated.
When the rotation shaft M rotates, the disk member 1 rotates around the rotation axis La. The bracket member 5 is in a non-rotating state in which the rotation is stopped by the guide shaft portion 81. The braking device 6 fixed to the bracket member 5 is also in a non-rotating state in which it does not rotate (revolve) around the rotation axis La.

  When the rotation of the rotating shaft M is stopped or when the stopped rotating shaft M is clamped and held, the electromagnet portion 61 is de-energized and the pair of brake shoes 66, 67 causes the braked disc portion 12 to move. Clamp and brake.

  Here, the rotation axis M is caused by shaft displacement factors such as heat, load, rattling due to dimensional accuracy, or a phenomenon that the rotation axis M moves to a position where the rotation axis M is electrically balanced by the magnetic force when energized in the motor. It may be displaced (expanded / contracted) in the rotational axis direction N rather than the state when it was constructed.

  When the rotation axis M is displaced in one axial center direction (a direction away from the braked device main body side), the brake unit Y (the disk member 1 and the disk member 1 and the same dimension as the rotation axis M is displaced (extended) in the axial center direction). The braking device 6) moves along the rotational axis La. In addition, even if the rotation shaft M is displaced (shortened) in the other direction of the shaft center (direction approaching the braked device main body side), the brake unit Y has the same dimensions as the displacement of the rotation shaft M in the other direction of the shaft center. (The disk member 1 and the braking device 6) move along the rotation axis La.

  In the brake structure of the conventional example shown in FIG. 4, the disk member 91 is fixed to the rotating shaft M on the brake side in an outer fitting manner, and the braking device 96 is fixed to the fixed other member 99 which is the casing of the machine body K. Was. Such a structure has, for example, the same dimension as the dimension in which the rotation axis M extends in one axial direction when the rotation axis M is displaced in one axial direction in the brake released state, and the disk member 91 also has the rotation axis. Move along La. However, the braking device 96 is not affected by the displacement of the rotating shaft M and does not move in one axial center direction. That is, the one plane of the braked disc portion 91a is in contact with one brake shoe 96a, and the brake shoe 96a is dragged.

However, in the present invention shown in FIGS. 1 to 3, even if the rotation shaft M is displaced in the brake released state, the disk member 1 and the braking device 6 are not relatively approached or separated (relatively fixed). ) The disk member 1 does not contact (interfere) with the brake shoes 66 and 67, and the brake shoes 66 and 67 do not drag.
Therefore, the axis center one-way predicted displacement dimension (amount) in which the rotation axis M may be displaced in one direction due to the shaft displacement factor, and the shaft center other-direction predicted displacement that may be displaced in the other direction. The air gap dimension S can be set smaller (narrower) than the dimension (amount).
For example, the rotation axis M may be displaced by 1 to 2 mm in one direction of the rotation axis or in the other direction of the rotation axis due to an axial displacement factor. Therefore, in the conventional braking structure, it is necessary to provide an air gap dimension S of 2 mm or more in order to prevent dragging. However, even if the braking drive body of the present invention is set to less than 1 mm, for example, 0.1 to 0.3 mm, drag does not occur.

  Further, when the rotating shaft M is displaced in the axial direction N, the bracket member 5 slides along the guide shaft portion 81 provided on the fixing member 7, and the brake unit Y is prevented from falling down. The brake unit Y is displaced together with the rotating shaft M while being held in the posture. That is, the brake unit Y translates with respect to the rotation axis La in a side view.

In the present invention, the design can be changed, and the guide shaft portion 81 may be provided in the bracket member 5 and the guide receiving hole portion 82 may be provided in the fixing member 7. The fixing structure of the disk member 1 and the rotating shaft M may be spline coupling or the like. The bearing member 3 may be a metal collar member, an oil-free bush, a roller bearing, or the like. Further, if the bracket member 5 is not slidable along the rotational axis La relative to the disk member 1 and is rotatable relative to the rotational axis La, the number of bearing members 3 and the attachment structure are as follows. Be free. The braking device 6 includes a brake shoe (shoe) 67 that can be contacted and separated from one plane (end surface) of the braked disk portion 12 of the disk member 1 and a brake that can be contacted and separated from the other plane (end surface) of the braked disk portion 12. As long as it has a shoe (shoe) 66 and can be braked by sandwiching the braked disk portion 12, a non-illustrated example may be used. The rotating shaft M is an output shaft for supplying power to the industrial machine, a braking shaft provided separately from the output shaft, or the like. A plurality of guide receiving hole portions 82 or guide shaft portions 81 may be provided in the bracket member 5, and one having an arrangement suitable for the construction site may be selected and used.

  As described above, the braking structure according to the present invention includes the disk member 1 that is fixedly fitted to the rotating shaft M on the brake side and the rotating shaft mounting boss portion 11 of the disk member 1 via the bearing members 3 and 3. And a bracket member 5 that is attached in an outer fitting shape and is rotatable around the axis La of the rotation axis M relative to the disk member 1, and a brake that is fixed to the bracket member 5 and clamps the disk member 1 for braking. A brake unit Y including the device 6 and a fixing member 7 attached to the other fixing member G. The bracket member 5 is disposed between the bracket member 5 and the fixing member 7 along the axis La. Therefore, the air gap dimension S is constant (set value) even if the rotation axis M on the braked side is displaced in the direction N of the rotation axis. ) And pull the brake shoes 66 and 67. Sliding is prevented, thereby preventing the generation of noise (sliding sound pads) it is possible to improve the durability. The air gap dimension S can be set smaller than the predicted displacement (expansion / contraction) dimension of the rotation axis M, and the operation noise can be reduced, and the impact and vibration during operation can be reduced. Further, a strong braking force (brake shoe pressing force) can be obtained. In addition, precise positioning work at the construction site is unnecessary, and construction can be performed easily and quickly.

  Further, the slide detent means 8 includes a guide shaft portion 81 that protrudes from one of the bracket member 5 and the fixing member 7 and a guide receiver that is provided on the other of the bracket member 5 and the fixing member 7 and into which the guide shaft portion 81 is inserted. Since the shaft center Lb of the guide shaft portion 81 is disposed in parallel with the shaft center La of the rotation shaft M, the rotation shaft M expands and contracts in the rotation axis direction N due to an axial displacement factor. In addition, the parallel movement along the rotational axis La can be smoothly performed while the brake unit Y is held in the normal posture. The brake unit Y can be slid and moved so as to correspond to the expansion and contraction of the rotation shaft M while reliably preventing the bracket member 5 from rotating about the rotation axis La. Construction can be performed easily and quickly.

DESCRIPTION OF SYMBOLS 1 Disc member 3 Bearing member 5 Bracket member 6 Braking device 7 Fixing member 8 Slide detent member
11 Rotating shaft mounting boss
51 through holes
73 Adjuster bolt
81 Guide shaft
82 Guide receiving hole
88 Sliding bearing member G Other fixed member La Shaft center Lb Shaft center M Rotating shaft Y Brake unit

Claims (2)

A disk member (1) fixed to the rotating shaft (M) on the braked side in an outer fitting manner, and a rotating shaft mounting boss (11) of the disk member (1) via a bearing member (3) (3). A bracket member (5) which is attached in an outer fitting shape and is rotatable around the axis (La) of the rotating shaft (M) relative to the disk member (1), and the bracket member (5) A brake unit (Y) comprising: a braking device (6) that is fixed to the disc member (1) and brakes the disc member (1).
A fixing member (7) attached to the other fixing member (G),
Between the bracket member (5) and the fixing member (7), a slide detent means (8) for holding the bracket member (5) slidably along the axis (La) and preventing detent. the setting,
The slide detent means (8) includes a guide shaft portion (81) protruding from one of the bracket member (5) and the fixing member (7), the bracket member (5) and the fixing member. A guide receiving hole (82) provided on the other side of the member (7) into which the one guide shaft (81) is inserted,
The fixing member (7) includes a plurality of adjuster bolts (73) for level adjustment,
A brake structure characterized in that the shaft center (Lb) of the guide shaft portion (81) is arranged in parallel to the shaft center (La) of the rotating shaft (M) by adjusting the adjuster bolt (73). . The guide receiving hole (82) has a sliding slide bearing member (88) fitted into a through hole (51) provided in the other of the bracket member (5) and the fixing member (7). The braking structure according to claim 1, wherein the braking structure is formed by an inner peripheral surface of the member (88) .

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