Torque limiter

Abstract

The present disclosure relates to a torque limiter comprising: a cover plate adapted to be driven for rotation about an axis of rotation and comprising a carrier ring and a plurality of tabs integrally formed, the tabs comprising carrier teeth axially spaced from the carrier ring by a distance; the pressing ring is arranged between the bearing ring and the bearing teeth in the axial direction; the driven disc is clamped between one of the bearing ring and the bearing teeth and the pressing ring in a sliding manner; and an elastic member axially disposed between the other of the carrier ring and the carrier tooth and the compression ring and biasing the compression ring toward the driven disc, in which the torque limiter further includes an inertia increasing portion disposed on the cover plate.

Description

Technical Field

[0001] The present disclosure relates to a torque limiter and a transmission assembly including the torque limiter. In particular, the torque limiter has an inertia increasing portion capable of increasing the moment of inertia of the torque limiter. Background Art

[0002] The torque generated by a motor vehicle engine is usually not constant and often fluctuates. This non-constant torque can be transmitted to the gearbox, causing vibration of the gearbox and thus generating particularly undesirable noises or impacts. To reduce the adverse effects of vibration and improve the driving comfort of the motor vehicle, it is known to be equipped with a torque fluctuation absorption mechanism in the motor vehicle powertrain. The torque fluctuation absorption mechanism can allow the fluctuations in the torque generated by the motor vehicle engine to be restricted and absorbed. The torque fluctuation absorption mechanism can include a flywheel, a torsional damper, and a torque limiter. The flywheel is directly fastened to the crankshaft of the engine and has a large moment of inertia, capable of storing and releasing torque, making the torque output of the engine smoother. The torque limiter is connected to the flywheel and can limit the torque fluctuations exceeding the maximum torque allowed by the torsional damper. The torsional damper is then connected to the torque limiter, which usually absorbs and reduces the fluctuations in torque through a spring structure.

[0003] The torque limiter generally includes a torque limiter cover fixedly connected to the flywheel and a driven disk connected to the torsional damper. When the torque fluctuation exceeds the maximum torque, the driven disk slides relative to the torque limiter cover, thereby restricting the transmitted torque. It is known that the torque limiter cover consists of two cover plates riveted together in the axial direction, and the driven disk is clamped between the two cover plates. This double-cover-plate type torque limiter cover has a large mass, which can also provide a certain moment of inertia and smooth the torque output of the engine in cooperation with the flywheel. However, the double-cover-plate type torque limiter cover also increases the component cost, making the torque limiter more expensive as a whole. In addition, in order to make the connection between the two cover plates firm and uniform, the number of rivets used for riveting is usually large, for example, 12 or more rivets are used. Using a large number of rivets will complicate the assembly process of the torque limiter, and there may be situations such as lost rivets and poor riveting quality, and additional control costs for the riveting process are generated.

[0004] Therefore, there is an urgent need for a torque limiter that has both a low cost and a sufficiently large moment of inertia. Summary of the Utility Model

[0005] Therefore, the present disclosure aims to solve the above problems, and its purpose is to provide a novel torque limiter that can be manufactured and assembled in a simple and cost-saving manner and has a sufficiently large moment of inertia.

[0006] The above object is achieved by a torque limiter according to an embodiment of the present disclosure. The torque limiter includes: a cover plate adapted to be driven to rotate about a rotation axis, and the cover plate includes an integrally formed bearing ring and a plurality of tabs, and the tabs include bearing teeth axially spaced apart from the bearing ring by a certain distance; a pressure ring axially disposed between the bearing ring and the bearing teeth; a driven disk slidably clamped between one of the bearing ring and the bearing teeth and the pressure ring; an elastic member axially disposed between the other of the bearing ring and the bearing teeth and the pressure ring, and biasing the pressure ring toward the driven disk, wherein the torque limiter further includes an inertia increasing portion disposed on the cover plate.

[0007] One object of the present disclosure is to provide a torque limiter that can be manufactured and assembled in a simple and cost-saving manner and has a sufficiently large moment of inertia. The cover plate of the torque limiter according to the present disclosure includes an integrally formed bearing ring and bearing teeth, and the pressure ring, the elastic member, and the driven disk are all held between the bearing ring and the bearing teeth. Therefore, the cover plate according to the present disclosure is formed as a torque limiter cover in a single component form, thereby simplifying the structure of the torque limiter and reducing the cost of components. In addition, since there is no need to assemble by riveting or the like, the assembly of the torque limiter according to the present disclosure becomes more convenient, reducing its manufacturing cost. As the name implies, the inertia increasing portion disposed on the cover plate can increase the moment of inertia of the cover plate, so that the integral cover plate has a sufficient moment of inertia, compensating for the reduction in the moment of inertia caused by omitting one cover plate.

[0008] The torque limiter according to the present disclosure may also have one or more of the following features individually or in combination.

[0009] According to an alternative embodiment of the present disclosure, the cover plate further includes a flange located radially outside the bearing ring and the tabs, and at least a part of the inertia increasing portion is located radially outside the flange. According to the above features, the inertia increasing portion is disposed at a radially outer portion of the cover plate, away from the rotation axis, which helps to increase the moment of inertia of the inertia increasing portion.

[0010] According to an alternative embodiment of the present disclosure, the inertia increasing portion includes a curled edge formed by inverting the radially outer edge of the flange. The inertia increasing portion formed by such a curled edge is located at the radially outermost portion of the cover plate, maximizing the moment of inertia of the inertia increasing portion.

[0011] According to an alternative embodiment of the present disclosure, the curled edge is inverted from the flange toward the bearing ring.

[0012] According to an alternative embodiment of the present disclosure, the curled edge axially extends beyond the bearing ring.

[0013] According to an alternative embodiment of the present disclosure, the curled edge turns from the flange towards the load-carrying teeth.

[0014] According to an alternative embodiment of the present disclosure, the curled edge axially extends to a position substantially flush with the load-carrying teeth.

[0015] According to an alternative embodiment of the present disclosure, the inertia increasing portion includes a diameter increasing portion located radially outside the flange.

[0016] According to an alternative embodiment of the present disclosure, the inertia increasing portion includes an inertia ring mounted on the flange.

[0017] According to an alternative embodiment of the present disclosure, the cover plate further includes a plurality of connecting portions that connect the load-carrying ring to the flange, and the tab includes a bent portion that connects the load-carrying teeth to the flange.

[0018] According to an alternative embodiment of the present disclosure, the bent portion is located radially outside the pressure ring, the driven disc, and the elastic member.

[0019] According to an alternative embodiment of the present disclosure, each tab is circumferentially arranged between two adjacent connecting portions, and the tab is spaced apart from the connecting portions by a predetermined distance on both sides in the circumferential direction. That is to say, the circumferential dimension of the tab is smaller than the interval dimension between two adjacent connecting portions. Preferably, the material of the tab and the material of the connecting portion are discontinuous before the tab is formed, but are spaced apart by the interval dimension, which facilitates the formation of the tab.

[0020] According to an alternative embodiment of the present disclosure, the length that the tab extends from the flange to the end of the load-carrying teeth is less than the length that the connecting portion extends from the flange to the load-carrying ring. According to the above technical features, the material of the tab and the material of the load-carrying ring are discontinuous before the tab is formed, thereby facilitating the formation of the tab.

[0021] According to an alternative embodiment of the present disclosure, the tab includes a weakening portion arranged at the connection between the bent portion and the load-carrying teeth. The weakening portion reduces the difficulty of bending the tab to form the load-carrying teeth.

[0022] According to an alternative embodiment of the present disclosure, the weakening portion is a weakening groove.

[0023] According to an optional embodiment of the present disclosure, the flange includes a plurality of bosses, which protrude in the direction axially away from the load-bearing ring, and each tab is arranged on one boss. According to the bosses, the axial distance between the connection portion between the tab and the flange and the load-bearing ring is increased. Thus, even when the axial length of the bent portion of the tab is compressed, it is possible to ensure that there is a sufficient axial distance between the load-bearing tooth and the load-bearing ring to accommodate the pressure ring, the driven disk and the elastic member. In addition, compressing the axial length of the bent portion can also increase the radial length of the load-bearing tooth, ensuring that the load-bearing tooth can extend radially to a position radially opposite to at least a portion of the load-bearing ring to clamp the pressure ring, the driven disk and the elastic member.

[0024] According to an optional embodiment of the present disclosure, the pressure ring has a plurality of radially extending anti-rotation teeth, and the anti-rotation teeth can be inserted between two adjacent connecting parts. According to this technical solution, if relative sliding in the circumferential direction occurs between the pressure ring and the cover plate, the anti-rotation teeth can abut against the connecting parts to prevent excessive sliding of the pressure ring. In other words, the anti-rotation teeth play a role in limiting the relative sliding between the pressure ring and the cover plate in the circumferential direction.

[0025] According to an optional embodiment of the present disclosure, each anti-rotation tooth is composed of two half teeth, and each half tooth abuts against one of the two adjacent connecting parts. Thus, the anti-rotation tooth can eliminate the relative sliding between the pressure ring and the cover plate as much as possible, and the size of the half tooth is not too large.

[0026] According to an optional embodiment of the present disclosure, the cover plate has a plurality of anti-rotation grooves, each of which is formed to be circumferentially arranged between two adjacent connecting portions and axially arranged between the load-bearing teeth and the load-bearing ring, and the anti-rotation teeth can be inserted into the corresponding anti-rotation grooves. According to this technical solution, if relative sliding in the circumferential direction occurs between the pressure ring and the cover plate, the anti-rotation teeth can abut against the anti-rotation grooves to prevent excessive sliding of the pressure ring. In other words, the anti-rotation teeth and the anti-rotation grooves play a role in limiting the relative sliding between the pressure ring and the cover plate in the circumferential direction.

[0027] According to an optional embodiment of the present disclosure, each anti-rotation tooth consists of two half teeth, and each half tooth abuts against one of two adjacent connecting parts.

[0028] According to an optional embodiment of the present disclosure, the flange includes a plurality of bosses, the bosses protrude in a direction axially away from the carrying ring, and each tab is arranged on one boss. BRIEF DESCRIPTION OF THE DRAWINGS

[0029] The above and other features and advantages of the present disclosure will become more apparent from the following detailed description of exemplary embodiments in conjunction with the accompanying drawings, and the description and drawings are for exemplary purposes only and do not limit the scope of the present disclosure in any way. The following drawings are not deliberately drawn to scale in actual size, and the emphasis is on showing the gist of the present disclosure. In the figures:

[0030] Figure 1 is a schematic diagram of a transmission assembly according to an embodiment of the present disclosure, and the transmission assembly includes a torsion limiter.

[0031] Figure 2 is Figure 1 an exploded view of the shown transmission assembly.

[0032] Figure 3 is Figure 1 a cross-sectional view of the shown transmission assembly.

[0033] Figure 4 is Figure 3 a partial cross-sectional view of the shown transmission assembly, in which the torsion limiter is shown in detail.

[0034] Figure 5 shows Figure 3 the cover plate of the torsion limiter in the shown embodiment.

[0035] Figure 6 shows the cover plate of the torsion limiter according to another embodiment of the present disclosure.

[0036] Figure 7 shows the cover plate of the torsion limiter according to still another embodiment of the present disclosure.

[0037] Figure 8 shows the retaining ring of the torsion limiter according to an embodiment of the present disclosure.

[0038] Figure 9 shows the elastic member of the torsion limiter according to an embodiment of the present disclosure.

[0039] In each figure, the same or similar components are denoted by the same reference numerals. Detailed Description of the Embodiments

[0040] In order to make the objectives, technical solutions, and advantages of the embodiments of the present disclosure clearer, the technical solutions of the embodiments of the present disclosure will be clearly and completely described below in conjunction with the drawings of the embodiments of the present disclosure.

[0041] Unless otherwise defined, technical terms or scientific terms used herein shall have the ordinary meanings as understood by those of ordinary skill in the art to which this disclosure pertains. The words such as "a", "an", or "the" used in the specification and claims of this patent application of the disclosure do not denote a limitation of quantity either, but rather mean that there is at least one. Words such as "comprising" or "including" mean that the elements or items appearing before this word cover the elements or items listed after this word and their equivalents, without excluding other elements or items. Directions such as "axial", "radial", and "circumferential" are defined with respect to the rotation axis X of the torque limiter. The axial direction is the direction in which the rotation axis X extends, the radial direction is the direction perpendicular to the rotation axis X, and the circumferential direction is the circumferential direction around the rotation axis X.

[0042] Figure 1 is a schematic view of a transmission assembly 1 according to an embodiment of the present disclosure. Figure 2 is Figure 1 an exploded view of the shown transmission assembly.

[0043] The transmission assembly 1 can be used to transmit torque between the engine and the gearbox of a motor vehicle. The transmission assembly 1 can be divided into two parts: a torque limiter 100 and a torsional damper 200. The torque limiter 100 is connected to the crankshaft of the vehicle engine and is driven by the crankshaft to transmit torque about the rotation axis X. The torsional damper 200 is generally located inside the torque limiter 100 and outputs the torque transmitted by the torque limiter 100 to the gearbox of the motor vehicle. The torque limiter 100 has a predetermined maximum torque, and even when the torque generated by the engine exceeds this maximum torque, the torque transmitted to the torsional damper 200 will not exceed this maximum torque.

[0044] Referring to Figure 1 and Figure 3 , the torsional damper 200 has an input portion 210, an output portion 220, and four springs 230 arranged to be compressed circumferentially between the input portion 210 and the output portion 220. The input portion 210 is fixed to the driven disk 30 of the torque limiter 100 to receive the torque transmitted from the torque limiter 100. The springs 230 are helical springs, one end of which is acted on by the input portion 210, and the other end acts on the output portion 220 to transmit the torque from the input portion 210 to the output portion 220. The springs 230 can absorb and reduce the fluctuations in the torque through compression and elongation.

[0045] Further referring to Figure 1 and Figure 3 and in combination with Figure 2 and Figure 5, the torque limiter 100 includes an integrally formed cover plate 10 adapted to be driven to rotate about a rotation axis X. Such a cover plate 10 can be formed by stamping, casting, or the like. Specifically, the cover plate 10 includes a flange 11, a carrier ring 12, a plurality of tabs 13, and a plurality of connecting portions 16 that connect the carrier ring 12 to the flange 11. In this embodiment, the flange 11 includes a plurality of through holes evenly distributed on its outer periphery, which can be used to fix the cover plate 10 to a flywheel (not shown) by screws or the like. The carrier ring 12 and the tabs 13 are integrally formed with the flange 11 and thus rotate together about the rotation axis X. The tabs 13 include load-carrying teeth 14 and a bent portion 15 that connects the load-carrying teeth 14 to the flange 11. The load-carrying teeth 14 of the tabs 13 are axially spaced apart from the carrier ring 12 by a predetermined distance. Specifically, both the bent portion 15 and the connecting portion 16 have a certain axial extension length, such that the load-carrying teeth 14 and the carrier ring 12 are respectively located on both axial sides of the flange 11.

[0046] Reference Figure 4 and in combination with Figure 3 and Figure 5 , an inertia increasing portion 50 is further provided on the cover plate 10 for increasing the moment of inertia of the integrally formed cover plate 10. The inertia increasing portion 50 is an additional material increasing portion on the cover plate 10. In Figure 4 the illustrated exemplary embodiment, the inertia increasing portion 50 is disposed at the radially outermost edge of the cover plate 10. Specifically, the flange 11 is located radially outside the carrier ring 12 and the tabs 13, and the inertia increasing portion 50 is constituted by a curled edge 51 formed by flipping the radially outer edge of the flange 11. In Figure 4 the illustrated embodiment, the curled edge 51 is flipped from the flange 11 toward the carrier ring 12 and axially extends beyond the carrier ring 12. The torque limiter 100 has a larger dimension in the axial direction on the side of the carrier ring 12 and is mounted to a flywheel (not shown) on this side. Therefore, there is a larger space on this axial side, and the curled edge 51 can extend with a larger axial length, increasing the moment of inertia that the inertia increasing portion 50 can increase.

[0047] Reference Figure 5, in the circumferential direction, the tab 13 of the cover plate 10 is arranged between two adjacent connecting portions 16. Preferably, the tab 13 is spaced apart from the connecting portion 16 by a predetermined distance on both sides in the circumferential direction. In addition, the length of the tab 13 extending from the flange 11 to the end of the load-bearing tooth 14 is less than the length of the connecting portion 16 extending from the flange 11 to the load-bearing ring 12. That is to say, if the cover plate 10 is flattened, the tab 13 is only connected to other parts of the cover plate 10 through the bending portion 15, and its side and end are spaced apart from other parts of the cover plate 10. The tab 13 with this structure can be formed by multiple stamping operations. For example, a U-shaped groove can be first stamped on the cover plate 10, and then the part surrounded by the U-shaped groove is stamped to form the tab 13. Compared with forming the tab by single stamping, stamping out the U-shaped groove first weakens the connection strength between the part surrounded by the U-shaped groove and the rest of the cover plate 10, making it easier to stamp out the tab 13.

[0048] The pressure ring 20 is axially arranged between the load-bearing ring 12 and the load-bearing tooth 14, and the driven disk 30 is slidably clamped between the load-bearing ring 12 and the pressure ring 20 by an elastic member 40 axially arranged between the load-bearing tooth 14 and the pressure ring 20. The elastic member 40 is supported by the load-bearing tooth 14 and presses the pressure ring 20, so that the driven disk 30 presses against the load-bearing ring 12. It is conceivable that the driven disk 30 is slidably clamped between the load-bearing tooth 14 and the pressure ring 20 by an elastic member 40 axially arranged between the load-bearing ring 12 and the pressure ring 20. The elastic member 40 is supported by the load-bearing ring 12 and presses the pressure ring 20, so that the driven disk 30 presses against the load-bearing tooth 14.

[0049] In the radial direction, the bending portion 15 of the tab 13 is located radially outside the pressure ring 20, the driven disk 30 and the elastic member 40. That is to say, the connecting portion of the tab 13 and the flange 11 is located radially outside the pressure ring 20, the driven disk 30 and the elastic member 40. The load-bearing tooth 14 of the tab 13 extends radially inward, preferably extending to at least partially axially oppose the load-bearing ring 12. In particular, the projection of the load-bearing tooth 14 in the axial direction partially coincides with the load-bearing ring 12, which helps to firmly hold the pressure ring 20, the driven disk 30 and the elastic member 40 between the load-bearing ring 12 and the load-bearing tooth 14.

[0050] Reference Figure 4 , the first axial distance of the load-bearing tooth 14 from the flange 11 is determined by the axial extension length of the bending portion 15, and the second axial distance of the load-bearing ring 12 from the flange 11 is determined by the axial extension length of the connecting portion 16. The sum of the first and second axial distances is the axial distance between the load-bearing tooth 14 and the load-bearing ring 12. The pressure ring 20, the driven disk 30 and the elastic member 40 are all accommodated within this axial distance.

[0051] Figure 6An alternative embodiment of the cover plate 10 is shown. In this embodiment, the inertia increasing portion 50 of the cover plate 10 is also constituted by a curled edge 51 formed by inverting the radial outer edge of the flange 11. The difference is that the curled edge 51 is inverted from the flange 11 towards the load bearing teeth 14. The torque limiter 100 has a smaller dimension in the axial direction on the side of the load bearing teeth 12 and is easily restricted by other components (such as the gearbox) of the vehicle powertrain. Therefore, there is less space available for the curled edge 51 to extend on this axial side, and the curled edge 51 axially extends to a position substantially flush with the load bearing teeth 14.

[0052] In some designs of the transmission assembly 1, the second axial distance between the load bearing ring 12 and the flange 11 of the cover plate 10 is restricted (as Figure 7 shown). In this case, in order to accommodate the pressure ring 20, the driven disk 30, and the elastic member 40, it is necessary to increase the first axial distance between the load bearing teeth 14 and the flange 11. However, for the cover plate 10 formed by stamping, the total length of the tab 13 is limited. If the first axial distance is increased by increasing the axial extension length of the bending portion 15, then the radial extension length of the load bearing teeth 14 needs to be shortened. This may cause the load bearing teeth 14 to not be able to extend to the radial position axially opposite to the load bearing ring 12, which is not conducive to the retention of the pressure ring 20, the driven disk 30, and the elastic member 40 between the load bearing ring 12 and the load bearing teeth 14.

[0053] For this reason, in Figure 7 the embodiment shown, the cover plate 10 forms a plurality of bosses 11a on the flange 11. The bosses 11a protrude in the direction axially away from the load bearing ring 12, and the tab 13 is formed on the bosses 11a. The height by which the bosses 11a protrude compensates for the axial distance between the load bearing teeth 14 and the load bearing ring 12, eliminating the need to increase the axial extension length of the bending portion 15, thereby ensuring that the load bearing teeth 14 can extend to the radial position axially opposite to the load bearing ring 12. In addition, in Figure 7 the embodiment shown, the inertia increasing portion 50 of the cover plate 10 is composed of a diameter increasing portion 52 located radially outside the flange 11. That is, the flange 11 has an additional increased diameter to increase the mass of the cover plate 10 and improve the moment of inertia of the cover plate 10.

[0054] In the embodiments of the inertia increasing portion 50 described above, the inertia increasing portion 50 is all constituted by an integral component of the cover plate 10. It can be understood that the inertia increasing portion 50 can also be a separate component separated from the cover plate 10. For example, the inertia increasing portion 50 can be formed by installing an inertia on the flange 11 of the cover plate 10.

[0055] Figure 8 The pressure ring 20 is shown. The pressure ring 20 includes a plurality of anti-rotation teeth 21 extending radially. Refer to Figure 3 and Figure 4, in the assembled structure of the torque limiter 100, the anti-rotation teeth 21 are inserted between two adjacent connecting parts 16. That is, when assembling the torque limiter 100, the angle of the retaining ring 20 is oriented such that the gap between the anti-rotation teeth 21 and the two connecting parts 16 is aligned. If relative sliding occurs between the retaining ring 20 and the cover plate 10, the anti-rotation teeth 21 will abut against the connecting parts 16, preventing further sliding of the retaining ring 20. Specifically, the anti-rotation teeth 21 are composed of two half teeth 21a, and each half tooth 21a abuts against one of the two adjacent connecting parts 16 respectively to eliminate relative sliding as much as possible. Alternatively, the width of the anti-rotation teeth 21 can also be set to be approximately equal to the gap between the adjacent connecting parts 16. Therefore, the anti-rotation teeth 21 function to position the retaining ring 20 in the circumferential direction.

[0056] In an alternative embodiment not shown in the drawings, a plurality of anti-rotation grooves may be provided on the cover plate 10, and each anti-rotation groove is formed to be circumferentially arranged between two adjacent connecting parts 16 and axially arranged between the load-carrying teeth 14 and the load-carrying ring 12. The anti-rotation teeth 21 of the retaining ring 20 can be inserted into the corresponding anti-rotation grooves to achieve angular positioning between the retaining ring 20 and the cover plate 10.

[0057] Figure 9 Then the elastic member 40 is shown. The elastic member 40 has the form of a Belleville spring. Refer to Figure 4 , in the assembled structure of the torque limiter 100, the elastic member 40 presses against the load-carrying teeth 14 and the retaining ring 20 respectively on both axial sides. The elastic member 40 is compressed in the axial direction, thereby applying an elastic pressing force on the retaining ring 20. By changing the parameters of the elastic member 40, the magnitude of this pressing force can be adjusted, and further the maximum torque that the torque limiter 100 can transmit can be adjusted.

[0058] With the above structure, the cover plate 10, the retaining ring 20 and the elastic member 40 of the torque limiter 100 can be driven by the flywheel to rotate together, and they jointly constitute the input side of the torque limiter 100. The torque output of the torque limiter 100 to the torsional damper 200 is achieved through the driven disk 30.

[0059] The torque limiter 100 as described above can be assembled in a simple manner. First, an integrally formed cover plate 10 is provided, which has a flange 11, a carrier ring 12, a tab 13, and a connecting portion 16 that connects the carrier ring 12 to the flange 11. In particular, the tab 13 has a structure that axially extends upward integrally from the flange 11 at this time, without forming a bending portion 15 and a load-bearing tooth 14. Then, the driven disk 30, the pressure ring 20, and the elastic member 40 are sequentially placed axially into the cover plate 10 and supported by the carrier ring 12. The connection position of the tab 13 and the flange 11 (i.e., the position of the bending portion 15) can ensure that the driven disk 30, the pressure ring 20, and the elastic member 40 are axially placed in position without being obstructed by the tab 13. In addition, when placing the pressure ring 20, its angular position is adjusted so that the anti-rotation teeth 21 are aligned with the gaps between the two connecting portions 16. Finally, the tab 13 is bent to form a bending portion 15 and a load-bearing tooth 14, and the pressure ring 20, the driven disk 30, and the elastic member 40 are axially held between the carrier ring 12 and the load-bearing tooth 14. In addition, the torsional damper 200 can be first installed on the driven disk 30 and then the driven disk 30 is assembled. Optionally, the torsional damper 200 is installed after the torque limiter 100 is assembled. Thus, the step of riveting the two cover plates of the torque limiter 100 can be omitted, while facilitating the installation of the driven disk, the pressure ring, and the elastic member, thereby saving the cost and time consumed in assembling the torque limiter 100 and improving the assembly success rate.

[0060] The bending of the tab 13 can be carried out by a specially designed workpiece. A weakening portion can also be provided at the connection of the bending portion 15 and the load-bearing tooth 14 on the tab 13 to facilitate the bending of the tab 13. Exemplarily, the weakening portion can have the form of a weakening groove. It can be understood that the weakening portion can also have other forms suitable for reducing the material strength at the connection of the bending portion 15 and the load-bearing tooth 14. For example, the weakening portion can be a weakening hole extending a certain length along the connection inside the tab 13. When stamping the cover plate 10, a step of separately stamping or extruding such a weakening portion can be provided.

[0061] Certain features, structures, or characteristics in one or more embodiments of the present disclosure can be appropriately combined.

[0062] The above is an explanation of the present disclosure and should not be considered as a limitation thereof. Although several exemplary embodiments of the present disclosure have been described, those skilled in the art will easily understand that many modifications can be made to the exemplary embodiments without departing from the novel teachings and advantages of the present disclosure. Therefore, all such modifications are intended to be included within the scope of the present disclosure defined by the claims. It should be understood that the above is an explanation of the present disclosure, and the present disclosure should not be considered as limited to the specific embodiments disclosed, and modifications to the disclosed embodiments and other embodiments are intended to be included within the scope of the present disclosure.

Claims

1. A torque limiter (100), characterized in that: The torque limiter (100) comprises: a cover plate (10) adapted to be driven to rotate about a rotation axis (X), and comprising an integrally formed carrying ring (12) and a plurality of tabs (13), wherein the tabs (13) comprise carrying teeth (14) axially spaced from the carrying ring (12); A pressure ring (20), the pressure ring (20) being arranged axially between the load-bearing ring (12) and the load-bearing teeth (14); A driven plate (30) slidably sandwiched between the load ring (12), one of the load teeth (14) and the pressure ring (20); an elastic member (40) which is axially arranged between the other of the load ring (12) and the load tooth (14) and the pressure ring (20) and biases the pressure ring (20) toward the driven disk (30), The torque limiter (100) further comprises an inertia increasing portion (50) arranged on the cover plate (10). The cover plate (10) further comprises a flange (11) located radially outside the carrying ring (12) and the tab (13), and at least a portion of the inertia increasing portion (50) is located radially outside the flange (11) or on the flange (11), and The inertia increasing portion (50) comprises any one of the following: a curled edge (51) formed by turning over the radial outer edge of the flange (11), a diameter increasing portion (52) located at the radial outer side of the flange (11), or an inertia ring installed on the flange (11).

2. The torque limiter (100) according to claim 1, characterized in that: The bead (51) is turned over from the flange (11) toward the carrier ring (12).

3. The torque limiter (100) according to claim 2, characterized in that: The bead (51) extends axially beyond the carrier ring (12).

4. The torque limiter (100) according to claim 1, characterized in that: The curled edge (51) is turned over from the flange (11) toward the load-bearing tooth (14).

5. The torque limiter (100) according to claim 4, characterized in that: The curled edge (51) extends axially to a position substantially flush with the load-bearing tooth (14).

6. The torque limiter (100) according to any one of claims 1 to 5, characterized in that: The cover plate (10) further comprises a plurality of connecting portions (16) connecting the carrier ring (12) to the flange (11), and The tab (13) comprises a bend (15) connecting the load-bearing tooth (14) to the flange (11).

7. The torque limiter (100) according to claim 6, characterized in that: The bent portion (15) is located radially outside the pressure ring (20), the driven disk (30) and the elastic member (40).

8. The torque limiter (100) according to claim 6, characterized in that: Each tab (13) is arranged between two adjacent connection parts (16) in the circumferential direction, and the tab (13) is spaced apart from the connection parts (16) at a predetermined distance on both sides in the circumferential direction.

9. The torque limiter (100) according to claim 6, characterized in that: The length of the tab (13) extending from the flange (11) to the distal end of the load-bearing tooth (14) is shorter than the length of the connecting portion (16) extending from the flange (11) to the load-bearing ring (12).

10. The torque limiter (100) according to claim 6, characterized in that: The tab (13) comprises a weakened portion arranged at the connection between the bent portion (15) and the load-bearing tooth (14).

11. The torque limiter (100) according to claim 10, characterized in that: The weakened portion is a weakened groove.

12. The torque limiter (100) according to claim 6, characterized in that: The flange (11) includes a plurality of bosses (11a) which protrude in an axial direction away from the carrier ring (12), and each tab (13) is arranged on one boss (11a).

13. The torque limiter (100) according to claim 6, characterized in that: The pressure ring (20) has a plurality of radially extending anti-rotation teeth (21), and the anti-rotation teeth (21) can be inserted between two adjacent connecting parts (16).

14. The torque limiter (100) according to claim 13, characterized in that: Each anti-rotation tooth (21) is composed of two half teeth (21a), and each half tooth (21a) abuts against one of two adjacent connecting parts (16).

15. The torque limiter (100) according to claim 13, characterized in that: The cover plate (10) has a plurality of anti-rotation grooves, each of which is formed to be circumferentially arranged between two adjacent connecting portions (16) and axially arranged between the load-bearing teeth (14) and the load-bearing ring (12), and the anti-rotation teeth (21) can be inserted into the corresponding anti-rotation groove.

16. The torque limiter (100) according to claim 15, characterized in that Each anti-rotation tooth (21) is composed of two half teeth (21a), and each half tooth (21a) abuts against one of two adjacent connecting parts (16).

17. The torque limiter (100) according to claim 15, characterized in that: The flange (11) includes a plurality of bosses (11a) which protrude in an axial direction away from the carrier ring (12), and each tab (13) is arranged on one boss (11a).

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