disc brake

Abstract

A disc brake is provided, comprising: a brake disc (13) disposed between a fixed disc (4) and an armature (5) of an electromagnet; a fastening bolt (14) for securing the electromagnet passes through a yoke (6) of the electromagnet, the armature, and the fixed disc in that order; a positioning sleeve (7) fitted onto the fastening bolt, one end of the positioning sleeve abutting the yoke and the other end abutting the fixed disc; the armature slidably fitted into the positioning sleeve; a ring-shaped upper convex edge formed on the disc surface of the fixed disc along the axial hole; a core hole of a floating disc (2) fitted onto the upper convex edge; an engagement opening for engagement with the positioning sleeve opened in the floating disc, the engagement opening and the positioning sleeve fitted together with a clearance maintained therebetween; one end of a tensile pressure sensor (3) axially attached to the fixed disc and the other end to the floating disc; the range of the clearance between the engagement opening and the positioning sleeve being within the maximum allowable deformation limit of the tensile pressure sensor. This design simplifies the structure of the disc brake, effectively reducing manufacturing costs and improving the market competitiveness of the product.

Description

[Technical Field]

[0001] The present invention relates to an electromagnetic brake, and more particularly to a disc brake capable of detecting braking torque in real time. [Background technology]

[0002] Motor brakes used in machinery such as wind turbines can gradually lose braking moment or even fail due to wear during use. Wind turbines are generally installed in remote mountainous areas, deserts, mountainous regions, or offshore locations, and their core power generating equipment is generally installed at the top of the generator's support column, making maintenance and inspection of the equipment extremely difficult and costly. Effective maintenance and inspection of wind turbines is a major challenge.

[0003] CN113374816A discloses a braking friction force detection device for a disc brake, including a disc clutch-type wheel-direction fine-motion mechanism and a tensile pressure sensor. The disc clutch-type wheel-direction fine-motion mechanism includes a fixed disc mounted on a motor, a torque transmission disc adjacent to the motor's brake disc, and a ball bearing mounted between the fixed disc and the torque transmission disc. The fixed disc and the torque transmission disc achieve wheel-direction fine-motion of the torque transmission disc during braking by clearance engagement between protrusions and grooves on their respective disc surfaces. The tensile pressure sensor includes an elastic body and a resistance strain gauge affixed to the elastic body. One end of the elastic body is connected to the fixed disc via a pin shaft, and the other end is connected to the torque transmission disc via a pin shaft. This braking friction force detection device achieves wheel-direction fine-motion of the torque transmission disc by engagement between protrusions and grooves on the mating disc surfaces of the fixed disc and the torque transmission disc, thereby transmitting braking torque and preventing damage to the tensile pressure sensor due to excessive rotation. The structure is relatively complicated, and the processing of the protrusions and grooves on the disk surface takes a long time and consumes a lot of material, which increases the manufacturing cost of the detection device and reduces its market competitiveness. Summary of the Invention [Problem to be solved by the invention]

[0004] An object of the present invention is to provide a disc brake capable of detecting braking torque in real time, in order to solve the problem that the braking friction force detection devices used in conventional disc brakes have a complex structure and high processing costs. [Means for solving the problem]

[0005] The object of the present invention is achieved as follows. a brake disc provided between a fixed disc and an armature of an electromagnet, and a clamping bolt for fixing the electromagnet passing through the yoke of the electromagnet, the armature and the fixed disc in that order, a positioning sleeve fitted onto the clamping bolt, one end of the positioning sleeve abutting against the yoke and the other end abutting against the fixed disc, the armature slidably fitted into the positioning sleeve, a ring-shaped upper convex edge formed on the disc surface of the fixed disc along an axial hole, a core hole of the floating disc fitted onto the upper convex edge, an engagement opening formed in the floating disc that engages with the positioning sleeve, the engagement opening and the positioning sleeve being fitted together with a clearance maintained therebetween, one end of a tensile pressure sensor journalled to the fixed disc and the other end journalled to the floating disc, and the range of the clearance between the engagement opening and the positioning sleeve is within the maximum allowable deformation limit of the tensile pressure sensor

[0006] Furthermore, a thrust needle roller bearing is provided between the floating disc and the fixed disc.

[0007] Furthermore, the floating disk is pressed against the disk surface of the fixed disk by a compression spring or a spring retainer plate.

[0008] Furthermore, the engagement opening is a notch formed on the edge of the floating disk or a circular hole formed on the disk surface of the floating disk.

[0009] Furthermore, an axial spline is formed on the inner wall of the axial hole of the brake disc, and a spline sleeve for connection to the motor output shaft is slidably fitted onto the spline in the axial hole of the brake disc. [Effects of the Invention]

[0010] In the present invention, the positioning sleeve attached to the fastening bolt not only positions the electromagnet and fixed disc on the motor casing with a certain spacing, but also serves as a floating disc rotation restriction member, restricting the axial rotation of the floating disc within the deformation limit of the elastic body of the tensile pressure sensor. This not only ensures that the tensile pressure sensor provides accurate and reliable detection data within its normal deformation limit, but also prevents the floating disc from rotating uncontrollably if the tensile pressure sensor is broken and loses its function, thereby preventing brake fade and ensuring the safe use of the disc brake.

[0011] The fixed disc and floating disc used in the present invention are both of conventional structure, and the disc surfaces do not have interlocking protrusions and grooves, which avoids long processing times and excessive material usage, thereby simplifying the structure of the disc brake and effectively reducing manufacturing costs, thereby improving the market competitiveness of the product. [Brief explanation of the drawings]

[0012] [Figure 1] 1 is a structural schematic diagram of a disc brake according to the present invention. [Figure 2] FIG. 2 is a cross-sectional view taken along the line AA in FIG. [Figure 3] FIG. 2 is a cross-sectional view taken along the line BB in FIG. [Figure 4] FIG. 4 is a partial cross-sectional view taken along the CC direction in FIG. 3. [Figure 5]FIG. 1 is a structural diagram showing how a floating disc is pressed by a spring retainer plate. DETAILED DESCRIPTION OF THE INVENTION

[0013] As shown in Figures 1, 2, and 3, the yoke 6, armature 5, and the coil 10 and brake spring 11, each fitted in a groove in the yoke, together constitute a brake-releasing electromagnet for a disc brake. A fastening bolt 14 passes through the yoke 6, armature 5, positioning sleeve 7, and fixed disk 4 in that order, securing the electromagnet and fixed disk 4 to the motor casing (not shown). One end of the positioning sleeve 7 abuts against the yoke 6, and the other end abuts against the fixed disk 4, thereby limiting the distance between the yoke 6 and the fixed disk 4 and ensuring sufficient clearance for the brake disc 13. The armature 5 has a through-hole that slidably fits onto the outer periphery of the positioning sleeve 7. A brake disc 13 is mounted between the fixed disk 4 and the armature 5. The inner wall of the axial hole of the brake disc 13 has an axial spline, and a spline sleeve 12, connected to the motor output shaft, slidably fits onto the spline in the axial hole of the brake disc. An adjustment pad 8 is provided at one end of the positioning sleeve 7 to adjust the moving clearance of the brake disc 13. Friction plates are provided on both sides of the brake disc 13, and friction braking is performed by the friction plates.

[0014] The surface of the fixed disc 13 facing the brake disc has a ring-shaped upper convex edge along the axial hole, and the core hole of the floating disc 2 is fitted onto the upper convex edge of the fixed disc 4. By providing a thrust needle roller bearing 9 between the floating disc 2 and the fixed disc 13, the rotational resistance and rotational friction of the floating disc 2 are reduced to the maximum extent possible, thereby improving the detection accuracy of the braking friction force and braking torque. The floating disc 2 can be pressed against the disc surface of the fixed disc 4 by a compression spring or spring retainer plate. Specifically, elastic pressing against the floating disc can be achieved by one of the following methods.

[0015] In the first method, an unthreaded hole is provided in the floating disc 2, and a screw passes through the unthreaded hole in the floating disc and threads into the threaded hole in the fixed disc 4, and the nut and washer of the screw work together to press the compression spring 1 against the disc surface of the floating disc 2.

[0016] In the second method, as shown in FIG. 4, an unthreaded hole is provided in the floating disk 2, and the bolt 15 passes through the threaded hole in the fixed disk 4 and the unthreaded hole in the floating disk 2 from the fixed disk 4 side, and is then exposed from the floating disk side, and the exposed end of the bolt presses the compression spring 1 against the disk surface of the floating disk 2 in cooperation with a nut 17 and a washer.

[0017] In the third method, as shown in FIG. 5, an unthreaded hole is provided in the floating disk 2, and the bolt 15 passes from the fixed disk 4 side through the threaded hole in the fixed disk and the unthreaded hole in the floating disk 2, and is then exposed from the floating disk side, and a spring retainer plate 16 is pressed onto the disk surface of the floating disk 2 at the exposed end by the cooperation of a nut 17 and a washer.

[0018] In FIG. 1, the floating disk 2 has an engagement opening that engages with the positioning sleeve 7, and this engagement opening and the positioning sleeve 7 are fitted together with a clearance maintained between them. The engagement opening of the floating disk 2 may be a notch opened on the edge of the floating disk, or a circular hole opened on the disk surface of the floating disk. The range of clearance between the engagement opening and the positioning sleeve 7 should be within the maximum allowable deformation range of the tensile pressure sensor. In addition, a fitting gap that is equal to or greater than the range of the clearance between the engagement opening and the positioning sleeve should be maintained between the unthreaded hole of the floating disk 2 and the screw / bolt.

[0019] The tensile pressure sensor 3 can be a sensor of conventional structure, and includes an elastic body that senses strain and a strain gauge that is attached to the elastic body to detect and transmit a strain detection signal. As shown in Figure 1, one end of the tensile pressure sensor 3 is connected to the fixed disk 4 via a pin shaft, and the other end of the tensile pressure sensor 3 is connected to the floating disk 2 via a pin shaft. When the electromagnet coil 10 loses power, the armature 5 is pressed against the brake disc 13, which rotates with the motor output shaft, by the action of the brake spring 11. At this time, friction plates on both sides of the brake disc 13 generate braking friction forces between the armature 5 and the floating disc 3, causing the floating disc 2 to rotate slightly in the direction of the wheel. This torque in the direction of the wheel pulls the tensile pressure sensor 3, causing minute strain. The strain gauge of the tensile pressure sensor 3 converts this minute strain into an electrical signal that reflects the magnitude of the braking friction force and outputs it externally. This enables real-time detection of the braking friction force of the disc brake. After detecting the braking friction force, the magnitude of the braking moment generated during the current braking operation can be calculated based on the structural dimensions of the brake disc using a moment calculation formula, thereby enabling real-time detection of the braking moment of the disc brake. [Explanation of symbols]

[0020] 1 compression spring 2 Floating Disc 3 Tensile pressure sensor 4 fixed disks 5 Armature 6 York 7 Positioning sleeve 8 Adjustment Pads 9. Thrust needle roller bearings 10 coils 11 Brake spring 12 Spline sleeve 13 Braking disc 14 Fastening bolt 15 volts 16 Spring retainer plate 17 Nut

Claims

1. A disc brake in which a brake disc is provided between a fixed disc and an armature of an electromagnet, and a fastening bolt for fixing the electromagnet passes through the yoke of the electromagnet, the armature, and the fixed disc in that order, a positioning sleeve fitted onto the fastening bolt, one end of the positioning sleeve abutting against the yoke and the other end abutting against the fixed disk, the armature slidably fitted with the positioning sleeve; a ring-shaped upper protruding edge is provided on the disk surface of the fixed disk along the axial hole, and the core hole of the floating disk is fitted onto the upper protruding edge; The floating disk has an engagement opening that engages with the positioning sleeve, and the engagement opening and the positioning sleeve are fitted together with a clearance maintained therebetween; One end of the tensile pressure sensor is axially attached to the fixed disc, and the other end is axially attached to the floating disc; The range of the clearance between the engagement opening and the positioning sleeve is within the maximum allowable deformation limit of the tensile pressure sensor. A disc brake characterized by:

2. A thrust needle roller bearing is provided between the floating disc and the fixed disc.

2. The disc brake according to claim 1.

3. The floating disk is pressed against the disk surface of the fixed disk by a compression spring or a spring retainer plate.

2. The disc brake according to claim 1.

4. The engagement opening is a notch formed on the edge of the floating disc or a circular hole formed on the disc surface of the floating disc.

2. The disc brake according to claim 1.

5. An axial spline is formed on the inner wall of the axial hole of the brake disc, and a spline sleeve for connection to the motor output shaft is slidably fitted with the spline in the axial hole of the brake disc.

2. The disc brake according to claim 1.

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