Adjusting device and disc brake

Abstract

The invention discloses an adjusting device and a disc brake, a ball groove clutch is arranged in the adjusting device, the ball groove clutch comprises a third ball and a ball bushing, and the ball bushing is provided with a fourth rolling surface; the conical clutch is provided with a conical lining, and the lower end face of the conical lining is provided with a third rolling face suitable for a third ball. Wherein the fourth rolling surface is provided with a first groove used for installing the third rolling ball, the third rolling surface is provided with a second groove which corresponds to the first groove and is used for installing the third rolling ball, and the rolling ball bushing and the conical clutch are separated by the third rolling ball. According to the technical scheme, the ball groove clutch can transmit the required specific torque to the cylindrical spring or the spring sleeve under different scene requirements, and the adjusting efficiency of the adjusting device is further improved.

Description

Technical Field

[0001] The present invention relates to the field of disc brakes, and 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 between the disc brake lining and disc during braking, a gap forms between the friction lining and disc. 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 manual resetting of the disc brake's clamping mechanism (hereinafter referred to as the resetting process), since the ratchet clutch of the existing adjustment device is in the shape of a ratchet (serrated), this structure has a large contact area and sliding friction, that is, a large friction coefficient. During the long adjustment and resetting process, it will produce large wear, causing the adjustment device to be unable to work normally and stably.

[0004] Therefore, there is an urgent need for an adjusting device and a disc brake that can work efficiently and stably. Summary of the Invention

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

[0006] According to one aspect of the present invention, there is provided an adjustment device for adjusting the wear of the brake friction lining and brake disc of a disc brake, comprising a drive shaft head, a ball ramp clutch, a cone clutch, a ball groove clutch, a cylindrical spring and a spring sleeve, wherein the ball groove clutch comprises a third ball and a ball bushing, and the ball bushing has a fourth rolling surface; the cone clutch has a cone bushing, and the lower end surface of the cone bushing has a third rolling surface suitable for the third ball; wherein the fourth rolling surface is provided with a first groove for mounting the third ball, and the third rolling surface is provided with a second groove corresponding to the first groove for mounting the third ball, and the ball bushing and the cone clutch are separated by the third ball.

[0007] Preferably, the first groove includes a slope forming the sidewall of the first groove and an arc forming the bottom of the first groove, the arc being tangentially connected to the slope; the second groove includes a second slope forming the sidewall of the second groove and a second arc forming the bottom of the second groove, the second arc being tangentially connected to the second slope. Preferably, the slope of the sidewall of the first groove has a driven slope angle of 30° to 60°; the second slope of the sidewall of the second groove has a working slope angle of 30° to 60°.

[0008] Preferably, the ball bushing has a first upper section and a first lower section, the outer side wall of the first upper section includes at least one first recessed structure recessed toward the axis, and the first lower section is a circumferential structure; the spring sleeve has at least one inward third protruding structure; wherein, when the ball bushing is installed in the spring sleeve, the third protruding structure of the spring sleeve is embedded in the first recessed structure of the ball bushing, so that the spring sleeve and the ball bushing form an anti-torsion connection.

[0009] Preferably, the spring sleeve further has a second recessed structure and a pressing component formed on the outer wall of the spring sleeve corresponding to the third protruding structure; wherein, by operating the pressing component, the spring sleeve is brought into pressing contact with the circumferential structure of the conical bushing.

[0010] Preferably, the conical bushing has a stepped structure, which divides the conical bushing into a second upper section and a second lower section; wherein the diameter of the second upper section is larger than the diameter of the second lower section. Preferably, the adjustment device further comprises a bearing race and a flange bushing; the flange bushing comprises an extension section and at least one first protruding structure, the first protruding structure being disposed on the extension section; the ball ramp clutch comprises 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 disposed 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 through the first through hole of the shift fork into the second through hole of the ramp valve plate; wherein 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; and no component is disposed in the second through hole of the ramp valve plate to block the rotation of the extension section.

[0011] 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.

[0012] 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.

[0013] 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.

[0014] 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.

[0015] According to another aspect of the present invention, a disc brake is provided, comprising the adjustment device described in any one of the above items.

[0016] Compared with the existing ratchet clutch that transmits torque to the cylindrical spring or spring sleeve, the present technical solution specially arranges a ball groove clutch to transmit torque to the cylindrical spring or spring sleeve in a ball rolling manner, thereby extending the service life of the adjusting device. In addition, the preset slope angle in the groove of the fourth ball enables the ball groove clutch to transmit the required specific torque to the cylindrical spring or spring sleeve under different scenario requirements, thereby further improving the adjustment efficiency of the adjusting device. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] Figure 1 This is a schematic structural diagram of the disc brake involved in this application;

[0018] Figure 2 This is a schematic diagram of the overall structure of the regulating device involved in this application;

[0019] Figure 3 This is a schematic structural diagram of the ball groove clutch involved in this application;

[0020] Figure 4 This is a schematic structural diagram of the ball bushing of the ball groove clutch involved in this application;

[0021] Figure 5 This is a schematic structural diagram of the tapered bushing involved in this application;

[0022] Figure 6 This is a schematic structural diagram of the spring sleeve involved in this application;

[0023] Figure 7 This is a schematic diagram of the ball ramp clutch structure involved in this application;

[0024] Figure 8A This is a schematic diagram of the rolling surface structure of the shift fork involved in this application;

[0025] Figure 8B This is a schematic diagram of the ball groove structure of the ramp valve plate involved in this application. DETAILED DESCRIPTION

[0026] 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.

[0027] 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.

[0028] 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.

[0029] 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 be referenced to, for example, the disclosure in DE19729024C1, which is incorporated into this application. Furthermore, the general structure and function of the adjustment device involved in this application can be referenced to the disclosure in DE102004037771A1, which is incorporated into this application. The following section of this application primarily illustrates the improvements to the structure and function of the adjustment device according to the present invention through exemplary embodiments described with reference to the accompanying drawings.

[0030] Figure 1 The structure and function of the disc brake can be referred to the disclosure of the corresponding specification of DE19729024C1. Figure 1 As 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.

[0031] The adjustment device 1 involved in this application is mainly used to compensate for the clearance caused by the brake friction of the disc brake. Figure 2 Schematic diagram of the overall structure of the regulating device 1 involved in this application. Figure 2As shown, the adjustment device 1 includes a drive shaft head 2, a bearing washer 3, a flange bushing 4, a ball ramp clutch 7, a cone clutch 9, a ball groove clutch 16, and a cylindrical spring 10 arranged in sequence, and the ball groove clutch 16 and the cylindrical spring 10 are located in a spring sleeve 11. wherein, the upper end portion of the drive shaft head 2 is located in the bearing washer 3, and 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 flange bushing 4 has a rolling surface for the ball 5 arranged below, the shift fork 6 has a rolling surface for the ball 5 arranged above, and the flange bushing 4 and the shift fork 6 are separated by the ball 5; the ball ramp clutch 7 comprises the shift fork 6 and the ramp valve plate 8, the ramp valve plate 8 has a rolling surface for the ball 40 arranged above, the shift fork 6 also has a rolling surface for the ball 40 arranged below, and the ramp valve plate 8 and the shift fork 6 are separated by the ball 40; the ramp valve plate 8 has a rolling surface for the ball 14 arranged below; The cone clutch 9 has a cone bushing 12, the cone bushing 12 has a rolling surface for cooperating with the ball 14, the rolling surface has an oblique groove 121 for accommodating the ball 14, and the ramp valve plate 8 and the cone bushing 12 are separated by the ball 14; the lower end surface of the cone bushing 12 has a rolling surface for the ball 41; the ball groove clutch 16 has a ball bushing 13, the upper end surface of the ball bushing 13 has the rolling surface for the ball 41, and the cone bushing 12 and the ball bushing 13 are separated by the ball 41; a cylindrical spring 10 is arranged in a spring sleeve 11 and supported between a two-tooth lock washer 15 and the ball bushing 13; an adjusting member (such as a nut or a rivet head) is arranged on the lower end of the main shaft 21 and is used to tension the cylindrical spring 10 and to axially concentrate the elements of the adjusting device 1.

[0032] Figure 3 This is a schematic structural diagram of the ball groove clutch involved in this application. Figure 4 Schematic diagram of the structure of the ball bushing of the ball groove clutch involved in this application. Figure 3 and Figure 4As shown, the ball groove clutch 13 includes a ball 41 and a ball bushing 13. The ball bushing 13 is divided into an upper section 1301 and a lower section 1302. The outer wall of the upper section 1301 of the ball bushing 13 includes at least one recessed structure 551 recessed toward the axis. The bottom of the recessed structure 551 is a step structure 55. The lower section 1302 of the ball bushing 13 is a circumference 53, which is a disc with no groove on the outer wall. The upper end surface of the upper section 1301 of the ball bushing 13 (i.e., the side facing the tapered bushing 12) includes a rolling surface 1342, at least one groove 1346 is provided on the rolling surface 1342, and the ball 41 is located in the groove 1346. The lower end surface of the tapered bushing 12 (i.e., the side facing the ball bushing 13) has a rolling surface 1242 suitable for the ball 41. The rolling surface 1242 is provided with a groove 1246 corresponding to the groove 1346. The ball 41 is located in the groove 1246 and separates the ball bushing 13 and the tapered bushing 12.

[0033] In the above embodiment, the groove 1346 includes a slope 1344 constituting the side wall of the groove 1346 and an arc 1345 constituting the bottom surface of the groove 1346, and the driven slope angle of the slope 1344 is γ. The driven slope angle is the angle between the slope 1344 and the horizontal plane. Preferably, the grooves 1346 of the ball bushing 13 and the grooves 1246 of the tapered bushing 12 are the same as the number of the balls 41, and correspond one to one. The advantage of such a setting is that the rolling space of the balls 41 is relatively smooth, and the balls 41 can rotate and transmit more smoothly in the space formed by the two fourth ball grooves, thereby improving the smoothness of the rotation of the ball groove clutch 16, thereby improving the adjustment efficiency of the adjustment device 1.

[0034] Figure 5 This is a schematic diagram of the structure of the tapered bushing involved in this application. Figure 5As shown, the conical bushing 12 of the conical clutch 9 includes a step structure 50, which divides the conical bushing 12 into an upper section 1201 and a lower section 1202. Preferably, the diameter of the upper section 1201 of the conical bushing 12 is greater than the diameter of the lower section 1202 of the conical bushing 12 (i.e., the step width of the step structure 50 is the difference between the diameters of the upper section and the lower section of the conical bushing 12). Preferably, the outer wall of the upper section 1201 of the conical bushing 12 is provided with the inclined groove 121 for accommodating the ball 14. Preferably, the groove 1246 includes a slope 1244 forming the sidewall of the groove 1246 and a circular arc 1245 forming the bottom of the groove 1246. The slope 1244 and the circular arc 1245 are tangentially connected, and the slope 1244 has a specific slope. More preferably, the slope 1244 of the sidewall of the groove 1246 is configured with a working slope angle β, i.e., the angle between the slope 1244 and a horizontal plane. The ball groove clutch 16 transmits a specific first torque to the cylindrical spring 10 and / or the spring sleeve 11 based on the working slope angle β and / or the driven slope angle γ.

[0035] In the above embodiment, compared to the prior art, the present application utilizes a structure in which the ball 41 matches the grooves 1246 and 1346, receiving torque from the cone clutch 9 through ball rolling and transmitting the torque to the external cylindrical spring 10 or spring sleeve 11. This not only transmits a certain torque, but also reduces wear and extends the service life of the adjustment device 1. Preferably, the present application utilizes a preset working slope angle β and / or driven slope angle γ, enabling the ball groove clutch 16 to transmit the required specific torque to the cylindrical spring 10 or spring sleeve 11 under the varying requirements of different scenarios, thereby improving the adjustment efficiency, stability, and service life of the adjustment device 1. More preferably, there is one or more ball 41 and groove 1246.

[0036] In the above embodiment, preferably, the working slope angle β is the same as the driven slope angle γ, so that the balls 41 can rotate and transmit more smoothly in the two groove spaces with the same slope, further improving the smoothness of the rotation of the ball groove clutch 16, thereby improving the adjustment efficiency of the adjustment device 1. Preferably, if it is desired to adjust the torque of the ball groove clutch 16, the working slope angle β and / or the driven slope angle γ can be adjusted.

[0037] In the above embodiment, preferably, the ball ramp clutch 7 has a second torque (i.e., a starting torque that causes the balls to move from the deep end to the shallow end), and the first torque of the ball groove clutch 16 is greater than the second torque. This arrangement has the advantage that when the disc brake is applied, the shift fork 6 rotates after receiving external torque, thereby driving the ball ramp clutch 7 to rotate. At this time, because the first torque of the ball groove clutch 16 is greater than the second torque of the ball ramp clutch 7, the ball groove clutch 16 rotates together with the cylindrical spring 10 or the spring sleeve 11, thereby rotating and moving the threaded sleeve of the disc brake forward until the brake disc and brake lining are fully in contact, completing the disc brake braking process and the clearance adjustment process of the adjustment device.

[0038] In the above embodiment, preferably, the slope 1244 is tangentially connected to the arc 1245, and the operating slope angle β ranges from 30° to 60°. Furthermore, the slope 1344 is tangentially connected to the arc 1345, and the driven slope angle γ ranges from 30° to 60°. This arrangement has the advantage that the 30° to 60° slope tangentially connected to the arc allows the ball 41 to rotate and transmit more smoothly, improving the smoothness of the operation of the ball groove clutch 16, thereby enhancing the stability and reliability of the adjustment device 1.

[0039] In the above embodiment, preferably, the number of the balls 41 is 10 to 30, and the diameter is 1 mm to 4 mm. This arrangement has the advantage that, when the ball groove clutch 16 is rotating, the rolling angle of each of the fourth balls is sufficiently small, allowing the adjustment device 1 to be precisely adjusted.

[0040] Figure 6 This is a structural stereogram of the spring sleeve involved in this application. Figure 6 As shown, the spring sleeve 11 has a first connection end adjacent to the stepped structure 50 of the tapered bushing 12 and a second connection end connected to the two-tooth lock washer 15. Near the first connection end, the spring sleeve 11 has at least one pressing component 51, at least one inwardly protruding structure 52, and a recessed structure 54 on the outer wall of the spring sleeve 11 corresponding to the protruding structure 52. The protruding structure 52 and the recessed structure 54 are formed by the outer wall of the connection end of the spring sleeve 11 being recessed toward the axis. The pressing component 51 can be located near the bottom of the recessed structure 54. By operating the pressing component 51, the spring sleeve 11 is pressed into contact with the lower circumference 53 of the tapered bushing 12, further enhancing the anti-torsion effect between the spring sleeve 11 and the tapered bushing 12.

[0041] In the above embodiment, preferably, the diameters of the upper section 1201 of the tapered bushing 12 and the stepped structure 50 are larger than the diameter of the spring sleeve 11, and the first connecting end of the spring sleeve 11 abuts the stepped structure 50. Thus, the spring sleeve 11 accommodates the lower section 1202 of the tapered bushing 12, the balls 41, the ball bushing 13, and the cylindrical spring 10. This arrangement has the advantage of arranging the ball groove clutch 16 and a portion of the tapered bushing 12 within the spring sleeve 11, which not only makes the tapered clutch 9 and the spring sleeve 11 more tightly connected, but also helps protect the ball groove clutch 16 and a portion of the tapered bushing 12 from damage caused by external impact, thereby enhancing the stability of the ball groove clutch 16.

[0042] In the above embodiment, preferably, when the ball bushing 13 is installed in the spring sleeve 11, the protrusion 52 fits snugly within the recess 551 of the ball bushing 13. More preferably, the bottom of the recess 54 abuts against the step 55 of the recess 551. This arrangement provides a torsion-resistant connection between the ball bushing 13 and the inner wall of the spring sleeve 11, increasing the torque dissipation between the ball bushing 13 and the spring sleeve 11 and further extending the torque dissipation between the two, thereby enabling the ball bushing 13 to drive the spring sleeve 11 in rotation.

[0043] In the above embodiment, the pressing member 51 preferably has a wing-shaped structure. More preferably, the pressing member 51 can press and contact the circumference 53 of the ball bushing 13, thereby ensuring more stable contact between the ball bushing 13 and the spring sleeve 11. This arrangement also has the advantage of further securing the position of the ball groove clutch 16, preventing it from disengaging from the spring sleeve 11 during rotation, thereby improving the stability of the ball groove clutch 16 and further enhancing the stability of the adjustment device 1.

[0044] Figure 7 This is a schematic diagram of the ball ramp clutch structure involved in this application. Figure 7 As shown, the ball ramp clutch 7 includes the shift fork 6, the ball 40 and the ramp valve plate 8. The shift fork 6 includes the ball 5, the speed change fork 61, the ball groove 62, the ring 63, the protruding structure 44 and the 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.

[0045] 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 8A ).

[0046] 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 significant impact, additional significant torsional torque, and torsional deformation on the flange bushing 4 during adjustment, 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.

[0047] 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 .

[0048] Figure 8A This is a schematic diagram of the rolling surface structure of the shift fork involved in this application. Figure 8B Schematic diagram of the ball groove structure of the ramp valve plate involved in this application. Figure 8A 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 8B 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 8B 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 8B 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.

[0049] In the above embodiment, the Figure 8A and Figure 8BThe 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.

[0050] In the above embodiment, the working rotation angle θ may be the same as or different from the working rotation angle α. Preferably, the working rotation angle θ may be the same as the working rotation angle α, so that the rotation of the shift fork 6 and the ramp valve plate 8 is synchronized with the rotation of the ramp valve plate 8 and the flange bushing 4, thereby improving the adjustment efficiency of the adjustment device 1.

[0051] According to another aspect of the present application, a disc brake is provided, comprising an adjusting device 1 according to any of the above embodiments. The advantages of the disc brake can be referred to the embodiments of the above adjusting device 1.

[0052] The foregoing descriptions of specific exemplary embodiments of the present invention have been presented 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 chosen and described in order to explain 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.

[0053] 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.

[0054] 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 ball ramp clutch, a cone clutch, a ball groove clutch, a cylindrical spring and a spring sleeve, characterized in that: The ball groove clutch includes a third ball and a ball bushing, wherein the ball bushing has a fourth rolling surface; The cone clutch has a cone bushing, and the lower end surface of the cone bushing has a third rolling surface suitable for a third ball; The fourth rolling surface is provided with a first groove for mounting the third ball, the third rolling surface is provided with a second groove corresponding to the first groove for mounting the third ball, and the ball bushing and the cone clutch are separated by the third ball.

2. The adjusting device according to claim 1, characterized in that: The first groove comprises a first slope constituting a side wall of the first groove and a first arc constituting a bottom of the first groove, wherein the first arc is tangentially connected to the first slope; The second groove includes a second slope constituting a side wall of the second groove and a second arc constituting a bottom of the second groove, and the second arc is tangentially connected to the second slope.

3. The adjusting device according to claim 2, characterized in that: The first slope of the side wall of the first groove has a driven slope angle of 30° to 60°; The second slope of the side wall of the second groove has a working slope angle of 30° to 60°.

4. The adjusting device according to claim 1, characterized in that: The ball bushing has a first upper section and a first lower section, the outer side wall of the first upper section includes at least one first concave structure concave toward the axis, and the first lower section is a circumferential structure; The spring sleeve has at least one third inwardly protruding structure; When the ball bushing is installed in the spring sleeve, the third protruding structure of the spring sleeve is embedded in the first recessed structure of the ball bushing, so that the spring sleeve and the ball bushing form an anti-torsion connection.

5. The adjusting device according to claim 4, characterized in that: The spring sleeve also has a second recessed structure and a pressing component formed on the outer wall of the spring sleeve corresponding to the third protruding structure; Wherein, the spring sleeve is brought into compression contact with the circumferential structure of the tapered bushing by operating the compression component.

6. The adjusting device according to claim 1, characterized in that: The tapered bushing has a step structure, and the step structure divides the tapered bushing into a second upper section and a second lower section; wherein a diameter of the second upper section is greater than a diameter of the second lower section.

7. The adjusting device according to any one of claims 1 to 6, characterized in that: The adjustment device also includes a bearing race and a flange bushing; The flange bushing comprises an extension section and at least one first protruding structure, wherein the first protruding structure is arranged on the extension section; The ball ramp clutch comprises 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; Wherein, the first protruding structure on the extension section cooperates with the second protruding structure in the first through hole to limit a first working rotation angle of the shift fork; The second through hole of the ramp valve plate is not provided with a component that blocks the rotation of the extension section.

8. The adjusting device according to claim 7, characterized in that: The length of the first protruding structure is shorter than the length of the extending section, and the first protruding structure does not enter the second through hole of the ramp valve plate when the extending section is inserted into the ball ramp clutch.

9. The adjusting device according to claim 7, 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.

10. The adjusting device according to claim 9, 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.

11. The adjusting device according to claim 10, 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; Wherein, the second ball rolling groove and the first ball rolling groove are arranged in the opposite direction.

12. A disc brake, characterized in that: Comprising the regulating device according to any one of claims 1-11.

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