Adjusting device and disc brake

Abstract

The utility model discloses an adjusting device and a disc brake. A flange bush of the adjusting device comprises an extension section and at least one first protruding structure, and the first protruding structure is arranged on the extension section; the ball ramp type clutch comprises a shifting fork and a ramp valve plate, the shifting fork is provided with a first through hole and at least one second protruding structure, the second protruding structures are arranged on the inner wall of the first through hole, and the ramp valve plate is provided with a second through hole. The extension section is inserted into the second through hole of the ramp valve plate through the first through hole of the shifting fork; a first protruding structure on the extending part section is matched with a second protruding structure in the first through hole to limit a first working rotation angle of the shifting fork; the second through hole of the ramp valve plate is not provided with a part which has a blocking effect on the rotation of the extension part section. Therefore, the flange bushing only directly receives the torque from the shifting fork, and the ramp valve plate is not in direct contact with the flange bushing to transmit the torque, so that the torque of the ramp valve plate acting on the flange bushing is reduced.

Description

Technical Field

[0001] The utility model relates to the field of disc brakes, in particular to an adjusting device and a disc brake. Background Art

[0002] Disc brakes are a common automotive braking system that converts the vehicle's kinetic energy into heat through friction and dissipates it into the surrounding air. The brake pads of this braking system are pressed against the rotating brake disc. When the driver depresses the brake pedal, the brake air chamber pushes against the clamping mechanism inside the caliper, creating friction between the pads and disc, thereby slowing the vehicle or stopping it. Furthermore, due to wear on the disc brake lining and disc during braking, the gap between the friction lining and disc increases. Therefore, manufacturers typically incorporate an adjustment device into disc brakes to automatically adjust this gap and manually reset the clamping mechanism when replacing the friction lining.

[0003] However, during the process of manually resetting the clamping mechanism of the disc brake (hereinafter referred to as the resetting process), the ball ramp clutch of the existing adjusting device will be subjected to a large torque and generate a large axial impact force, a large torsional torque and torsional deformation on the flange bushing, and further generate corresponding impact and torsional force on the bearing washer connecting the adjusting device and the disc brake. In severe cases, the adjusting device will be deformed and the clamping mechanism of the disc brake will be damaged, making the disc brake unable to be used normally.

[0004] Therefore, there is an urgent need for an adjusting device and a disc brake that can reduce the axial impact force or torsional force of the ball ramp clutch on the flange bushing during the adjustment process. Utility Model Content

[0005] The utility model aims to provide an adjusting device and a disc brake, which can solve the above technical problems.

[0006] According to one aspect of the utility model, an adjustment device for adjusting the wear of the brake friction lining and brake disc of a disc brake is provided, comprising a drive shaft head, a bearing race, a flange bushing, a ball ramp clutch, a cylindrical spring and a spring sleeve, the flange bushing comprising an extension section and at least one first protruding structure, the first protruding structure being arranged on the extension section; the ball ramp clutch comprising a shift fork and a ramp valve plate, the shift fork having a first through hole and at least one second protruding structure, the second protruding structure being arranged on the inner wall of the first through hole, and the ramp valve plate having a second through hole; the extension section of the flange bushing is inserted into the second through hole of the ramp valve plate through the first through hole of the shift fork; wherein the first protruding structure on the extension section cooperates with the second protruding structure in the first through hole to limit the first working rotation angle of the shift fork; and no component that blocks the rotation of the extension section is provided in the second through hole of the ramp valve plate.

[0007] Preferably, the length of the first protruding structure is shorter than the length of the extension section, and when the extension section is inserted into the ball ramp clutch, the first protruding structure does not enter the second through hole of the ramp valve plate.

[0008] Preferably, the ball ramp clutch further includes a first ball, the ramp valve plate has at least one first ball groove, the first ball is installed in the first ball groove, the shift fork and the ramp valve plate are separated by the first ball; the rolling of the first ball in the first ball groove limits the second working rotation angle of the ramp valve plate.

[0009] Preferably, the shift fork has at least one second ball groove on the side facing the ramp valve plate, and the second ball groove corresponds to the first ball groove in position, so that the first ball groove and the second ball groove form a space for the first ball to roll, thereby limiting the second working rotation angle of the ramp valve plate.

[0010] Preferably, the first ball groove includes a first end and a second end, and the second ball groove includes a third end and a fourth end; the groove depths of the first end and the second end of the first ball groove are different, and the depth gradually becomes shallower from the first end to the second end; the groove depths of the third end and the fourth end of the second ball groove are different, and the depth gradually becomes shallower from the third end to the fourth end; wherein, the second ball groove and the first ball groove are arranged in opposite directions.

[0011] Preferably, the ramp valve plate has a first rolling surface arranged below and suitable for the second ball; the adjustment device also includes a conical clutch, the conical clutch has a conical bushing, the conical bushing has a second rolling surface arranged on the upper end side and suitable for the second ball; the ramp valve plate and the conical bushing are separated by the second ball.

[0012] Preferably, the tapered bushing is disposed within the spring sleeve.

[0013] Preferably, the tapered bushing has a third rolling surface suitable for the third ball arranged on the lower end surface; the adjustment device also includes a ball groove clutch, the ball groove clutch has a ball bushing, and the ball bushing has a fourth rolling surface suitable for the third ball arranged on the upper end surface; the ball bushing and the tapered bushing are separated by the third ball.

[0014] Preferably, the ball bushing is arranged in the spring sleeve and forms a torsion-resistant connection with the inner wall of the spring sleeve.

[0015] According to another aspect of the present invention, a disc brake is provided, comprising any one of the above-mentioned adjustment devices.

[0016] In the present application, the flange bushing has an extended section and at least one first protruding structure, and the length of the first protruding structure is set in a targeted manner, so that during the automatic adjustment process of the adjustment device, the flange bushing only directly receives the torque from the fork, and the ramp valve plate no longer directly contacts the flange bushing to transmit the torque, thereby reducing the torque exerted by the ramp valve plate on the flange bushing and improving the stability of the adjustment device. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] Figure 1 Schematic diagram of the structure of a disc brake;

[0018] Figure 2 This is an overall structural diagram of the regulating device involved in this application;

[0019] Figure 3 This is a schematic diagram of the flange bushing structure involved in this application;

[0020] Figure 4 This is a schematic diagram of the ball ramp clutch structure involved in this application;

[0021] Figure 5A This is a schematic diagram of the rolling surface structure of the shift fork involved in this application;

[0022] Figure 5B This is a schematic diagram of the ball groove structure of the ramp valve plate involved in this application. DETAILED DESCRIPTION

[0023] The following describes in detail embodiments of the present application, examples of which are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present application, and are not to be construed as limiting the present application.

[0024] It will be understood by those skilled in the art that, unless expressly stated otherwise, the singular forms "a", "an", "said" and "the" used herein may also include the plural forms. It should be further understood that the term "comprising" used in the specification of the present application refers to the presence of the features, integers, steps, operations, elements and / or components, but does not exclude the presence or addition of one or more other features, integers, steps, operations, elements, components and / or groups thereof. It should be understood that when we refer to an element as being "connected" to another element, it may be directly connected to the other element, or there may be intermediate elements. In addition, the "connection" used here may include wireless connection. The term "and / or" used here includes all or any unit and all combinations of one or more associated listed items.

[0025] It will be understood by those skilled in the art that, unless otherwise defined, all terms (including technical and scientific terms) used herein have the same meaning as commonly understood by those skilled in the art to which this application belongs. It should also be understood that terms such as those defined in common dictionaries should be understood to have meanings consistent with their meanings in the context of the prior art and will not be interpreted in an idealized or overly formal sense unless specifically defined as herein.

[0026] The adjustment device involved in this application can be suitable for use in disc brakes, etc. The structure and function of the disc brake can refer to the disclosure of DE19729024C1, for example, and can be incorporated into this application. Furthermore, the general structure and function of the adjustment device involved in this application can refer to the disclosure of DE102004037771A1, which can be incorporated into this application. The following section of this application mainly explains the improvements to the structure and function of the adjustment device of this utility model through exemplary embodiments described with reference to the accompanying drawings.

[0027] Figure 1 The structure and function of the disc brake can be referred to the disclosure of the corresponding specification of DE19729024C1. Figure 1As shown, the disc brake 20 includes: an adjustment device 1, a brake disc 21, a brake caliper 22, a brake friction lining 23, a crossbeam 24, an adjustment shaft 25 (26), a pressure member 27, a sprocket 28, a chain 29, an eccentric wheel 30 and a torsion bar 31, wherein the torsion bar 31 has a driving member 32, and the driving member 32 and the shift fork 6 of the adjustment device 1 (refer to Figure 2 The adjusting device 1 is arranged in the adjusting shaft 25.

[0028] Figure 2 The schematic diagram of the overall structure of the regulating device involved in this application is shown in FIG. The regulating device 1 involved in this application is mainly used to compensate for the gap caused by the brake friction of the disc brake. Figure 2 As shown, the adjustment device 1 includes: a drive shaft head 2, a bearing race 3, a flange bushing 4, a ball ramp clutch 7, a cone clutch 9, a ball groove clutch 16, a cylindrical spring 10, a spring sleeve 11 and a two-tooth lock washer 15. The upper end of the drive shaft head 2 is located on the arc concave surface 301 of the bearing washer 3 (refer to Figure 3 ), the main shaft 21 of the drive shaft head 2 passes through the entirety of the adjusting device 1; the bearing race 3 is used to fix the adjusting device 1 in the brake caliper 22; the flange bushing 4 is connected to the bearing race 3 in a rotationally fixed manner; the ball ramp clutch 7 has a ramp valve plate 8, and the ramp valve plate 8 has a rolling surface for the balls 14 arranged on the lower end surface; the cone clutch 9 has a cone bushing 12, and the cone bushing 12 has a rolling surface for the balls 14 arranged on the upper end side surface, and the ramp valve plate 8 and the cone bushing 12 are separated by the balls 14. ; The above-mentioned conical bushing 12 has a rolling surface suitable for the ball 41 arranged on the lower end surface; the above-mentioned ball groove clutch 16 has a ball bushing 13, the above-mentioned ball bushing 13 has a rolling surface suitable for the above-mentioned ball 41 arranged on the upper end surface, and the above-mentioned ball bushing 13 is connected to the spring sleeve 11 in a torsionally fixed manner; the cylindrical spring 10, which is arranged in the spring sleeve 11 and supported on the two-tooth lock washer 15; the adjusting part (such as a nut or a rivet head), which is arranged on the lower end of the above-mentioned main shaft 21 and is used to tension the above-mentioned cylindrical spring 10 and to axially concentrate the elements of the above-mentioned adjusting device 1 together.

[0029] In the above embodiment, the ball bushing 13 is arranged in the spring sleeve 11, so that the ball bushing 13 and the inner wall of the spring sleeve 11 fit more tightly. The anti-torsion connection formed by the ball bushing 13 and the inner wall of the spring sleeve 11 increases the torque between the ball bushing 13 and the spring sleeve 11, and makes the torque consumption between the ball bushing 13 and the spring sleeve 11 longer.

[0030] In the above embodiment, the tapered bushing 12 is disposed in the spring sleeve 11 , so that the spring sleeve 11 protects the tapered bushing 12 from being damaged by external impact.

[0031] Figure 3 This is a schematic diagram of the flange bushing structure involved in this application. Figure 3 As shown, the bearing race 3 also has an arc surface 49 and a connecting piece 303. The upper side of the flange bushing 4 has an arc concave surface 48, and the lower side has a rolling surface suitable for the ball 5. The extension section 42 of the flange bushing 4 passes through the fork 6 and enters the ramp valve plate 8. The flange bushing 4 has a protruding structure 43, which is arranged on the extension section 42. The length of the protruding structure 43 is shorter than that of the extension section 42. When the extension section 42 is inserted into the ball ramp clutch 7, the protruding structure 43 does not enter the through hole 46 of the ramp valve plate 8. The protruding structure 43 can be a strip structure, and one or more strip structures can be arranged on the extension section 42. The side of the flange bushing 4 also has a bayonet 402 for cooperating with the connecting piece 303.

[0032] In the above embodiment, the arc surface 49 cooperates with the arc concave surface 48, and the arc concave surface 48 abuts against the arc surface 49 of the bearing washer 3. The connecting piece 303 cooperates with the bayonet 402, and the connecting piece 303 is engaged in the bayonet 402, so that the bearing race 3 and the flange bushing 4 are connected in a torsion-proof manner.

[0033] Figure 4 This is a schematic diagram of the ball ramp clutch structure involved in this application. Figure 4 As shown, the ball ramp clutch 7 includes a shift fork 6, a ball 40 and a ramp valve plate 8. The shift fork 6 includes a ball 5, a speed change fork 61, a ball groove 62, a ring 63, a protruding structure 44 and a through hole 45. The speed change fork 61 and the driving member 32 of the torsion bar 31 (see Figure 1) is connected, the ball groove 62 is provided between the circular ring 63 and the inner wall of the fork 6, the ball 5 is installed in the ball groove 62, the rolling surface of the flange bushing 4 is provided on one side of the fork 6, and the two are separated by the ball 5. The protruding structure 44 is provided on the inner wall of the through hole 45 and cooperates with the protruding structure 43 of the flange bushing 4. The number of the protruding structures 44 corresponds to the number of the protruding structures 43. The ramp valve plate 8 has a through hole 46 and at least one ball groove 64. The ball 40 is installed in the ball groove 64, and the side of the fork 6 facing the ramp valve plate 8 has a rolling surface suitable for the ball 40, and the ramp valve plate 8 and the fork 6 are separated by the ball 40. No component that blocks the rotation of the extension section is provided in the through hole 46 of the ramp valve plate 8.

[0034] In the above embodiment, the extension section 42 of the flange bushing 4 is inserted into the through hole 46 of the ramp valve plate 8 through the through hole 45 of the shift fork 6. The protruding structure 43 on the extension section 42 of the flange bushing 4 only extends into the through hole 45 of the shift fork 6, and does not extend into the through hole 46 of the ramp valve plate 8 (see FIG. Figure 2 Therefore, the protruding structure 43 on the extending section 42 of the flange bushing 4 only cooperates with the protruding structure 44 of the shift fork 6 to define a working rotation angle α (refer to Figure 5A ).

[0035] In the prior art, the protruding structure 43 on the extended section 42 of the flange bushing 4 passes through the entire ball ramp clutch 7 and acts together with the clutch ring of the cone clutch 9 to define a working rotation angle α. This configuration causes the adjusting device 1 to generate a large impact, additional large torsional torque, and torsional deformation on the flange bushing 4 during adjustment and reset, thereby adversely affecting the mounting point of the bearing washer 3 on the brake caliper 22. In the above embodiment, the protruding structure 43 on the extended section 42 of the flange bushing 4 is shortened. As a result, the ramp valve plate 8 does not need to directly contact the flange bushing 4, but instead relies on the balls 40 between the shift fork 6 and the ramp valve plate 8 for contact and interaction. This shortens the effective torque from the torque application point of the ramp valve plate 8 to the edge of the flange bushing 4, effectively reducing the torsional deformation and torsional torque of the flange bushing 4 and protecting the mounting point of the bearing washer 3.

[0036] In the above embodiment, one or more protruding structures 43 may be provided on the extension section 42 of the flange bushing 4 , and one or more protruding structures 44 of the shift fork 6 may also be provided corresponding to the number of the protruding structures 43 .

[0037] Figure 5A This is a schematic diagram of the rolling surface structure of the shift fork involved in this application. Figure 5B Schematic diagram of the ball groove structure of the ramp valve plate involved in this application. Figure 5A As shown, the rolling surface of the fork 6 has at least one ball groove 65, and the groove depth of one end 651 and the other end 652 of the ball groove 65 are different, and the depth gradually becomes shallower from the one end 651 to the other end 652. Figure 5B As shown, the groove depths of one end 641 and the other end 642 of the ball groove 64 of the ramp valve plate 8 are different, and the depth gradually becomes shallower from the one end 641 to the other end 642. The position of the ball groove 64 corresponds to the position of the ball groove 65, but the two are arranged in opposite directions, that is, the direction of the one end 651 corresponds to the direction of the other end 642, and the direction of the other end 652 corresponds to the direction of the one end 641. For example, when the adjustment device 1 is being adjusted, when the fork 6 moves in one direction (for example Figure 5B When the shift fork 6 rotates in the X direction (as shown in the figure), if the starting position of the ball 40 is in the space formed by the one end 651 and the one end 641, the ball 40 rolls from the one end 641 to the one end 642 in the ball groove 64 of the ramp valve plate 8, and at the same time rolls from the one end 651 to the other end 652 in the ball groove 65 of the shift fork 6. When the ball 40 rolls from the other end 641 to the one end 642 in the ball groove 64 of the ramp valve plate 8, the rotation of the shift fork 6 in this direction stops. When the shift fork 6 rotates in the opposite direction (for example, Figure 5B When the shift fork 6 rotates in the opposite direction (in the opposite direction of the X direction shown), the ball 40 rolls in the ball groove 64 of the ramp valve plate 8 from the other end 642 to the one end 641, and simultaneously rolls in the ball groove 65 of the shift fork 6 from the one end 652 to the other end 651. When the ball 40 rolls from the other end 642 to the one end 641 in the ball groove 64 of the ramp valve plate 8, the rotation of the shift fork 6 in the opposite direction stops. Therefore, the ball groove 65 of the shift fork 6 cooperates with the ball groove 64 of the ramp valve plate 8, allowing the ball 40 to roll within a certain range, thereby defining a working rotation angle θ.

[0038] In the above embodiment, the Figure 5A and Figure 5BThe structure of the ball groove 65 of the shift fork 6 and the ball groove 64 of the ramp valve plate 8 shown in the figure can gradually reduce the torsional moment between the shift fork 6 and the ramp valve plate 8, thereby further reducing the axial impact force generated on the flange bushing 4, thereby further effectively reducing the torsional deformation and torsional moment of the flange bushing 4, and protecting the mounting point of the bearing washer 3. In particular, when an emergency brake causes an overload on the brake, a large axial impact force is generated on the flange bushing 4. The above structure in this embodiment can effectively buffer the axial impact force through the movement of the balls, thereby providing an overload protection function.

[0039] In the above embodiment, the working rotation angle θ may be the same as or different from the working rotation angle α.

[0040] According to another aspect of the present invention, a disc brake is provided, comprising an adjusting device according to any one of the above embodiments. The advantages of the disc brake can be referred to the embodiments of the above adjusting device.

[0041] The foregoing descriptions of specific exemplary embodiments of the present invention are for purposes of illustration and description. These descriptions are not intended to limit the invention to the precise forms disclosed, and it is apparent that many modifications and variations are possible in light of the foregoing teachings. The exemplary embodiments have been selected and described for the purpose of explaining the specific principles of the invention and their practical application, thereby enabling those skilled in the art to make and utilize various exemplary embodiments of the invention and various alternatives and variations thereof.

[0042] Those skilled in the art will appreciate that the steps, measures, and schemes in the various operations, methods, and processes discussed in this application may be interchanged, modified, combined, or deleted. Furthermore, other steps, measures, and schemes in the various operations, methods, and processes discussed in this application may also be interchanged, modified, rearranged, decomposed, combined, or deleted. Furthermore, steps, measures, and schemes in the prior art that are similar to those disclosed in this application may also be interchanged, modified, rearranged, decomposed, combined, or deleted.

[0043] The above description is only part of the implementation methods of the present application. It should be pointed out that for ordinary technicians in this technical field, several improvements and modifications can be made without departing from the principles of the present application. These improvements and modifications should also be regarded as the scope of protection of the present application.

Claims

1. An adjusting device for adjusting the wear of a brake friction lining and a brake disc of a disc brake, comprising a drive shaft head, a bearing race, a flange bushing, a ball ramp clutch, a cylindrical spring, and a spring sleeve, characterized in that: The flange bushing includes an extension section and at least one first protruding structure, wherein the first protruding structure is provided on the extension section; The ball ramp clutch includes a shift fork and a ramp valve plate, wherein the shift fork has a first through hole and at least one second protruding structure, wherein the second protruding structure is arranged on the inner wall of the first through hole, and the ramp valve plate has a second through hole; The extended section of the flange bushing is inserted into the second through hole of the ramp valve plate through the first through hole of the shift fork; The first protruding structure on the extension section cooperates with the second protruding structure in the first through hole to define a first working rotation angle of the shift fork; No component that blocks the rotation of the extension section is provided in the second through hole of the ramp valve plate.

2. The adjustment device according to claim 1, characterized in that: The length of the first protruding structure is shorter than the length of the extending section. When the extending section is inserted into the ball ramp clutch, the first protruding structure does not enter the second through hole of the ramp valve plate.

3. The adjustment device according to claim 1, characterized in that: The ball ramp clutch further includes a first ball, the ramp valve plate has at least one first ball groove, the first ball is installed in the first ball groove, and the shift fork and the ramp valve plate are separated by the first ball; The rolling of the first ball in the first ball groove defines a second working rotation angle of the ramp valve plate.

4. The adjustment device according to claim 3, characterized in that: The shift fork has at least one second ball groove on the side facing the ramp valve plate, and the second ball groove corresponds to the first ball groove in position, so that the first ball groove and the second ball groove form a space for the first ball to roll, thereby limiting the second working rotation angle of the ramp valve plate.

5. The adjustment device according to claim 4, characterized in that: The first ball groove includes a first end and a second end, and the second ball groove includes a third end and a fourth end; The first end and the second end of the first ball groove have different groove depths, and the depth gradually becomes shallower from the first end to the second end; The groove depths of the third end and the fourth end of the second ball groove are different, and the depth gradually becomes shallower from the third end to the fourth end; The second ball rolling groove and the first ball rolling groove are arranged in opposite directions.

6. The regulating device according to any one of claims 1 to 5, characterized in that: The ramp valve plate has a first rolling surface arranged below and suitable for a second ball; The adjustment device further comprises a conical clutch, wherein the conical clutch comprises a conical bushing with a second rolling surface arranged on the side of the upper end and suitable for the second ball; The ramp valve plate and the tapered bushing are separated by the second ball.

7. The adjustment device according to claim 6, characterized in that: The tapered bushing is disposed within the spring sleeve.

8. The adjustment device according to claim 6, characterized in that: The tapered bushing has a third rolling surface arranged on the lower end surface and suitable for a third ball; The adjustment device further comprises a ball groove clutch having a ball bushing with a fourth rolling surface arranged on an upper end surface and suitable for the third ball; The ball bushing and the tapered bushing are separated by the third ball.

9. The adjustment device according to claim 8, characterized in that: The ball bushing is arranged in the spring sleeve and forms a torsion-resistant connection with the inner wall of the spring sleeve.

10. A disc brake, characterized in that: The regulating device comprises the regulating device according to any one of claims 1 to 9.

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