Clutch positioning mechanism, clutch and engine
By designing a clutch positioning mechanism including positioning tongue and pressing tongue, the problem of difficulty in accurately positioning the axial and radial directions of the special-shaped wedges in the prior art is solved, and high-precision positioning of the cage and wedges is achieved, and wear problems are avoided.
Patent Information
- Application Number
- CN202421730836.2
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2024-07-22
- Publication Date
- 2025-06-17
- Estimated Expiration
- 2034-07-22
AI Technical Summary
The prior art is difficult to take into account both the precise positioning of the axial and radial directions of the special-shaped wedge blocks, causing the cage to deviate from the central axis, thereby causing wear.
A clutch positioning mechanism is designed, including a cage, a first press plate and a second press plate. By combining the positioning tab and the pressing tab, the radial and axial positioning of the cage and the wedge is achieved.
This design can simultaneously take into account the precise positioning of the cage and wedge in the radial and axial direction, preventing the cage from deviating from the central axis and contacting the inner ring of the clutch and causing wear.
Smart Images
Figure CN222991978U_ABST
Abstract
Description
Technical Field
[0001] The present application relates to the technical field of mechanical transmission, and particularly to a clutch positioning mechanism, a clutch, and an engine. Background Art
[0002] A wedge-type overrunning clutch is a clutch that uses wedges and inner and outer raceways to form a friction pair, and uses special-shaped wedges instead of traditional rollers as wedging members.
[0003] In the related art, generally a cage is used to install the above-mentioned various special-shaped wedges, and two pressure plates are used to clamp the axial two sides of the special-shaped wedges respectively to achieve the axial positioning of the special-shaped wedges.
[0004] However, it is difficult to simultaneously achieve precise axial and radial positioning of the special-shaped wedges in the related art, which may cause the cage to tilt in a direction deviating from the central axis, and further cause the cage to contact and wear with the inner ring of the clutch. Summary of the Invention
[0005] Based on this, in view of the problem that it is difficult to simultaneously achieve precise axial and radial positioning of the special-shaped wedges in the related art, it is necessary to provide a clutch positioning mechanism, a clutch, and an engine.
[0006] On the one hand, the present application provides a clutch positioning mechanism, the clutch positioning mechanism includes a cage, a first pressure plate, and a second pressure plate. The cage has uniformly distributed mounting portions along its circumferential direction, and the mounting portions are used for mounting the wedges of the clutch. The first pressure plate and the second pressure plate are used to respectively press against the two axial sides of the wedge. The first pressure plate is uniformly distributed with at least two pressing tongues and at least two positioning tongues along its circumferential direction. The distribution diameter of the positioning tongues along the radial direction is greater than the distribution diameter of the pressing tongues along the radial direction, and axially, the positioning tongues and the pressing tongues are staggered from each other and form a compression distance. The pressing tongues can perform compression deformation relative to the positioning tongues along the axial direction within the compression distance.
[0007] When the above clutch positioning mechanism is in use, the positioning lug and the circumferential side of the second pressing plate are clamped to the side wall of the outer ring, achieving the effect of radially positioning the cage from both axial ends simultaneously. In this way, the cage can be prevented from skewing, so as to prevent the cage from wearing against the inner ring of the clutch. Further, since the radial distribution diameter of the positioning lug is larger than that of the pressing lug, the cage is only positioned by the positioning lug, while the pressing lug can be axially compressed and deformed to achieve axial positioning of the wedge block. In this way, the positioning parts are independent of each other, which helps to improve the positioning accuracy. Therefore, the above clutch positioning mechanism can simultaneously achieve precise positioning of the cage and the wedge block in both the radial and axial directions, which helps to prevent the problem that the cage deviates from the central axis direction and contacts the inner ring of the clutch, resulting in wear.
[0008] In one embodiment, the radial direction of the pressing lug deviates towards the side of the first pressing plate for pressing the wedge block, so that the radial direction of the pressing lug forms a deviation angle with the radial direction of the positioning lug.
[0009] In one embodiment, in the circumferential direction around the central axis of the first pressing plate, the length of the positioning lug is greater than the length of the pressing lug.
[0010] In one embodiment, the positioning lugs and the pressing lugs have the same number and are staggered in the circumferential direction of the first pressing plate around the central axis.
[0011] In one embodiment, the cage is rotationally symmetric about the center and is in a square wave shape along its extending direction.
[0012] On the other hand, the present application also provides a clutch, including the above clutch positioning mechanism. The clutch further includes at least two wedge blocks, an inner ring, an outer ring and a flywheel. The wedge blocks are clamped in the mounting portion. The first pressing plate and the second pressing plate respectively press against the two axial sides of the wedge blocks. The outer ring is sleeved on the inner ring. The wedge blocks and the cage are clamped between the inner ring and the outer ring. The circumferential side of the second pressing plate and the positioning lugs are clamped to the side wall of the outer ring. The outer ring is provided with an abutting ring surface. The pressing lugs press against the abutting ring surface. The flywheel and the outer ring are axially fixedly connected to each other, so that the flywheel axially presses against the positioning lugs and causes the pressing lugs to be axially compressed and deformed.
[0013] The above-mentioned clutch includes the above-mentioned clutch positioning mechanism. The positioning lug of the clutch positioning mechanism and the circumferential side of the second pressure plate are clamped to the side wall of the outer ring, achieving the effect of radially positioning the cage simultaneously from both axial ends. In this way, the skew of the cage can be prevented, so as to prevent the cage from wearing against the inner ring. Further, since the radial distribution diameter of the positioning lug is larger than that of the pressing lug, the cage is only positioned by the positioning lug, while the pressing lug can undergo compressive deformation along the axial direction to achieve the axial positioning of the wedge block. In this way, the positioning parts are independent of each other, which helps to improve the positioning accuracy. Therefore, the above-mentioned clutch can take into account the precise positioning of the cage and the wedge block in both the radial and axial directions, which helps to prevent the problem that the cage deviates from the central axis direction and contacts the inner ring of the clutch, resulting in wear.
[0014] In one embodiment, the circumferential sides of the second pressure plate and the positioning lug are both in contact with the side wall of the outer ring; or, a first positioning gap and a second positioning gap are respectively reserved between the circumferential sides of the second pressure plate and the positioning lug and the side wall of the outer ring.
[0015] In one embodiment, the value range of the first positioning gap is less than or equal to 0.2 mm.
[0016] In one embodiment, the value range of the second positioning gap is less than or equal to 1 mm.
[0017] On the other hand, the present application also provides an engine, which includes the above-mentioned clutch, and also includes a motor, an idler gear and an output crankshaft. The motor is drivingly connected to the idler gear, the idler gear is drivingly connected to the inner ring, and the output crankshaft is drivingly connected to the inner ring.
[0018] The above-mentioned engine includes the above-mentioned clutch, and the positioning lug of the clutch positioning mechanism and the circumferential side of the second pressure plate are clamped to the side wall of the outer ring, achieving the effect of radially positioning the cage simultaneously from both axial ends. In this way, the skew of the cage can be prevented, so as to prevent the cage from wearing against the inner ring. Further, since the radial distribution diameter of the positioning lug is larger than that of the pressing lug, the cage is only positioned by the positioning lug, while the pressing lug can undergo compressive deformation along the axial direction to achieve the axial positioning of the wedge block. In this way, the positioning parts are independent of each other, which helps to improve the positioning accuracy. Therefore, the above-mentioned engine can take into account the precise positioning of the cage and the wedge block in both the radial and axial directions, which helps to prevent the problem that the cage deviates from the central axis direction and contacts the inner ring of the clutch, resulting in wear. BRIEF DESCRIPTION OF THE DRAWINGS
[0019] Figure 1The front view of a partial mechanism of the engine in an embodiment of the present application.
[0020] Figure 2 is Figure 1 The sectional view of the shown mechanism at A - A.
[0021] Figure 3 is Figure 1 The schematic diagram of a partial structure in the shown mechanism.
[0022] Figure 4 The schematic diagram of the clutch positioning mechanism in an embodiment of the present application.
[0023] Figure 5 is Figure 3 The exploded view of...
[0024] Figure 6 is Figure 3 The top view of the shown structure.
[0025] Figure 7 is Figure 6 The sectional view of the shown structure at B - B when it is not pressed by the flywheel.
[0026] Figure 8 is Figure 7 The enlarged view at D.
[0027] Figure 9 is Figure 6 The sectional view of the shown structure at C - C when it is pressed by the flywheel.
[0028] Figure 10 is Figure 9 The enlarged view at E.
[0029] Figure 11 is Figure 9 The enlarged view at F.
[0030] Explanation of the reference numerals in the drawings
[0031] 10. Motor; 20. Idler gear; 30. Piston; 40. Output crankshaft; 50. Clutch; 51. Flywheel; 52. Wedge block; 53. Inner ring; 531. Large tooth; 54. Outer ring; 541. Contact ring surface; 55. Clutch positioning mechanism; 551. First pressing plate; 5511. Positioning lug; 5512. Pressing lug; 5513. First flange; 552. Second pressing plate; 5521. Second flange; 553. Cage; 5531. Mounting portion. Detailed implementation manners
[0032] To make the above objects, features, and advantages of the present application more apparent and understandable, the following provides a detailed description of the specific embodiments of the present application in conjunction with the accompanying drawings. A lot of specific details are set forth in the following description to facilitate a full understanding of the present application. However, the present application can be implemented in many other ways different from those described herein, and those skilled in the art can make similar improvements without departing from the connotation of the present application. Therefore, the present application is not limited by the specific embodiments disclosed below.
[0033] In the description of the present application, it should be understood that if terms such as "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. appear, the orientation or positional relationship indicated by these terms is based on the orientation or positional relationship shown in the accompanying drawings. These are only for the convenience of describing the present application and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as a limitation to the present application.
[0034] In addition, if terms such as "first" and "second" appear, these terms are only for descriptive purposes and should not be construed as indicating or implying relative importance or implicitly specifying the quantity of the indicated technical features. Thus, features defined with "first" and "second" may explicitly or implicitly include at least one such feature. In the description of the present application, if the term "plurality" appears, the meaning of "plurality" is at least two, such as two, three, etc., unless otherwise specifically and clearly defined.
[0035] In the present application, unless otherwise clearly specified and limited, if terms such as "install", "connect", "join", "fix", etc. appear, these terms should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, or integrated; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, and it can be the communication inside two elements or the interaction relationship between two elements, unless otherwise clearly limited. For those of ordinary skill in the art, the specific meanings of the above terms in the present application can be understood according to specific circumstances.
[0036] In this application, unless otherwise clearly specified and defined, if there is a description such as a first feature being "on" or "under" a second feature, its meaning can be that the first and second features are in direct contact, or the first and second features are in indirect contact through an intermediate medium. Moreover, the first feature being "above", "over" and "on top of" the second feature can be that the first feature is directly above or obliquely above the second feature, or simply means that the first feature has a higher horizontal height than the second feature. The first feature being "under", "beneath" and "underneath" the second feature can be that the first feature is directly below or obliquely below the second feature, or simply means that the first feature has a lower horizontal height than the second feature.
[0037] It should be noted that if an element is referred to as being "fixed to" or "disposed on" another element, it can be directly on the other element or there can also be an intermediate element. If an element is considered to be "connected to" another element, it can be directly connected to the other element or there may be an intermediate element at the same time. If so, the terms "vertical", "horizontal", "up", "down", "left", "right" and similar expressions used in this application are only for the purpose of illustration and do not represent the only implementation.
[0038] Refer to Figure 1 and Figure 2 , Figure 1 shows a front view of a part of the mechanism of the engine in an embodiment of the present application. Figure 2 is Figure 1 a cross-sectional view of the mechanism shown at A-A. The engine provided in an embodiment of the present application includes a motor 10, an idler wheel 20, an output crankshaft 40 and a clutch 50. Among them, a piston 30 is connected to the output crankshaft 40. The motor 10 is drivingly connected to the idler wheel 20. The idler wheel 20 is connected to the inner ring 53 of the clutch 50, and the output crankshaft 40 is drivingly connected to the inner ring 53. It can be understood that the piston 30 is used to compress and do work in a cylinder block (not shown), and the output mechanism of the engine is not described in detail herein.
[0039] When the engine needs to be started, first, the motor 10 needs to be started. The motor 10 drives the idler wheel 20 to rotate, and then the idler wheel 20 drives the large gear 531 of the inner ring 53 of the clutch 50 to rotate. Finally, the output crankshaft 40 is driven to rotate, and the output crankshaft 40 drives the piston 30 to compress the combustion gas to ignite.
[0040] In the process of starting the engine as described above, it is required that the clutch is not allowed to slip before the engine is ignited, and it is ensured that the torque of the motor 10 is transmitted to the output crankshaft 40 and drives the output crankshaft 40 to drive the piston 30 to cycle to ignite the engine.
[0041] After the engine is ignited, the rotational speed of the output crankshaft 40 will be much higher than that of the motor 10. At this time, if the clutch is not disengaged, it will drive the motor 10 to rotate in reverse. Moreover, when the engine is working, the rotational speed of the output crankshaft 40 is very high and far exceeds the bearing range of the motor 10. The excessive rotational speed will cause noise and also damage the motor 10. Therefore, after the engine is started, it is necessary to disconnect the connection between the output crankshaft 40 and the large gear 531 of the inner ring 53 to prevent the output crankshaft 40 from driving the idle gear 20 and the motor 10 to rotate in reverse. In other words, when the rotational speed of the output crankshaft 40 exceeds the driving rotational speed for starting the motor 10, the clutch will slip (the output crankshaft 40 slips relative to the inner ring 53), and the driving relationship between the output crankshaft 40 and the motor 10 will be disengaged. The above is the starting process of the engine provided by this application.
[0042] Further, in combination with Figure 3 、 Figure 4 Figure 5 as shown. Based on the above engine structure, this application provides a clutch 50 and a clutch positioning mechanism 55. Among them, Figure 3 is Figure 1 a partial structural schematic diagram of the clutch 50 in the engine shown, specifically, Figure 3 shows a partial structural schematic diagram of the clutch 50 provided by this application with the flywheel 51 omitted. Figure 4 is Figure 3 a structural schematic diagram of the clutch positioning mechanism 55 of the clutch 50 shown. Figure 5 is Figure 3 an exploded view of
[0043] First, in combination with Figure 3 and Figure 5 as shown, a clutch 50 provided by this application includes at least two wedge blocks 52, an inner ring 53, an outer ring 54, a flywheel 51 (omitted in Figure 3 - Figure 5 ) and the clutch positioning mechanism 55 provided by this application. Further, in combination with Figure 4 and Figure 5 as shown, the clutch positioning mechanism 55 includes a cage 553, a first pressing plate 551 and a second pressing plate 552. The cage 553 has uniformly distributed mounting portions 5531 along its circumferential direction. The wedge blocks 52 are clamped in the mounting portions 5531. The first pressing plate 551 and the second pressing plate 552 respectively press against the axial two sides of the wedge blocks 52. The outer ring 54 is sleeved on the inner ring 53. The wedge blocks 52 and the cage 553 are clamped between the inner ring 53 and the outer ring 54. The first pressing plate 551 is uniformly distributed with at least two positioning tongues 5511 and at least two pressing tongues 5512 along its circumferential direction. The circumferential side edges of the second pressing plate 552 and the positioning tongues 5511 are clamped to the side wall of the outer ring 54. The outer ring 54 is provided with an abutting ring surface 541, and the pressing tongues 5512 press against the abutting ring surface 541.
[0044] Furthermore, the radial distribution diameter of the positioning lug 5511 is larger than that of the pressing lug 5512. Axially, the positioning lug 5511 and the pressing lug 5512 are staggered from each other to form a compression gap. The flywheel 51 and the outer ring 54 are fixedly connected to each other axially, so that the flywheel 51 axially presses against the positioning lug 5511, and the pressing lug 5512 is axially compressed and deformed relative to the positioning lug 5511 within the compression gap.
[0045] When the clutch positioning mechanism 55 is in use, the circumferential side edges of the positioning lug 5511 and the second pressing plate 552 are clamped to the side wall of the outer ring 54, achieving the effect of radially positioning the cage 553 simultaneously from both axial ends. In this way, the cage 553 can be prevented from skewing, so as to prevent the cage 553 from wearing against the inner ring 53 of the clutch 50. Further, since the radial distribution diameter of the positioning lug 5511 is larger than that of the pressing lug 5512, the cage 553 is only positioned by the positioning lug 5511, while the pressing lug 5512 can be axially compressed and deformed to axially position the wedge 52. In this way, the positioning parts are independent of each other, which helps to improve the positioning accuracy. Therefore, the above clutch positioning mechanism 55 can simultaneously achieve precise positioning of the cage 553 and the wedge 52 in the radial and axial directions, which helps to prevent the problem that the cage 553 deviates from the central axis direction and contacts the inner ring 53 of the clutch 50 to cause wear.
[0046] Regarding the clutch positioning mechanism 55 provided in the present application, the following embodiments are further included.
[0047] In some embodiments, the radial direction of the pressing lug 5512 deviates towards the side of the first pressing plate 551 for pressing the wedge 52, so that the radial direction of the pressing lug 5512 forms a deviation angle with the radial direction of the positioning lug 5511.
[0048] Specifically, in combination with Figure 7 and Figure 8 as shown, Figure 7 is Figure 6 a cross-sectional view at B-B of the structure shown in the state where it is not pressed by the flywheel 51. Figure 8 is Figure 7Enlarged view at D. As can be seen from the figure, when the flywheel 51 and the outer ring 54 are not pressed together, since the positioning lug 5511 and the pressing lug 5512 are staggered from each other, the positioning lug 5511 is slightly higher than the pressing lug 5512. The pressing lug 5512 can abut against the abutting ring surface 541 of the outer ring 54, while the positioning lug 5511 is used to axially adhere to the end face of the flywheel 51. At this time, since the flywheel 51 and the outer ring 54 are not pressed together, the pressing lug 5512 does not deform, and a deviation angle is formed between the radial direction of the pressing lug 5512 and the radial direction of the positioning lug 5511. It should be noted that the pressing action between the flywheel 51 and the outer ring 54 can be achieved by bolt fixation, that is, before the flywheel 51 and the outer ring 54 are fixed to each other, there is an installation gap between the flywheel 51 and the outer ring 54, so that the pressing lug 5512 can abut against the abutting ring surface 541 of the outer ring 54 in an undeformed state.
[0049] Combined with Figure 9 and Figure 10 shown, Figure 9 is Figure 6 a cross-sectional view at C-C of the structure shown in the state of being pressed by the flywheel 51; Figure 10 is Figure 9 an enlarged view at E. When the flywheel 51 and the outer ring 54 are locked together, one side surface of the positioning lug 5511 moves downward while adhering to the end face of the flywheel 51 and under the downward pressure of the flywheel 51, so that the pressing lug 5512 can generate a downward elastic deformation relative to the abutting ring surface 541 of the outer ring 54, and then adhere to the abutting ring surface 541 of the outer ring 54. In this way, under the elastic action of the pressing lug 5512, the axial limit of the wedge block 52 can be maintained.
[0050] In this embodiment, a deviation angle is formed between the radial direction of the pressing lug 5512 and the radial direction of the positioning lug 5511, so as to achieve the effect that the pressing lug 5512 can press against the abutting ring surface 541 of the outer ring 54 to undergo elastic deformation, and then maintain the axial limit of the wedge block 52. The above structure is simple and reliable.
[0051] Refer back to Figure 4, in some embodiments, in the circumferential direction around the central axis of the first pressing plate 551, the length of the positioning lug 5511 is greater than the length of the pressing lug 5512. In this way, the contact area between the positioning lug 5511 and the side wall of the outer ring 54 can be ensured, and further the stability of the positioning lug 5511 during radial positioning can be ensured. And the pressing lug 5512 is designed to be smaller than the positioning lug 5511 in length, so as to be able to reduce the pressing force required for the pressing lug 5512 to undergo elastic deformation when the flywheel 51 and the outer ring 54 are pressed against each other. Understandably, the axial force required to drive the pressing lug 5512 to undergo elastic deformation along the axial direction is positively correlated with the length of the pressing lug 5512. Therefore, the length of the positioning lug 5511 is designed to be greater than the length of the pressing lug 5512, so that while ensuring the radial positioning stability, and without affecting the axial positioning function of the pressing lug 5512, the axial force required for the pressing lug 5512 to undergo elastic deformation along the axial direction can be reduced to improve the structural reliability.
[0052] In some embodiments, the positioning lugs 5511 and the pressing lugs 5512 have the same number and are staggered in the circumferential direction of the first pressing plate 551 around the central axis. In this way, it can be ensured that whether in radial positioning or axial positioning, the force can be balanced, thereby improving the positioning accuracy of the cage 553 and the coaxiality of the cage 553 and the inner ring 53, and preventing the problem that the cage 553 is skewed and then abrades with the inner ring 53.
[0053] Continuing to combine Figure 4 As shown, in some embodiments, the cage 553 is rotationally symmetric about the center and is square-wave shaped along its extending direction. In this way, uniformly distributed mounting portions 5531 can be formed. And in terms of structure, the square-wave shaped cage 553 can achieve the effect of being alternately snap-fitted with the first pressing plate 551 and the second pressing plate 552, which helps to improve the limiting effect on the cage 553.
[0054] Specifically, the first pressing plate 551 is provided with first flanges 5513 at intervals in its circumferential direction, the second pressing plate 552 is provided with second flanges 5521 at intervals in its axial direction, and the first flanges 5513 and the second flanges 5521 are alternately arranged, so that the cage 553 can be alternately snap-fitted with the first flanges 5513 and the second flanges 5521.
[0055] In some embodiments, the clutch 50 provided in the present application includes the clutch positioning mechanism 55 of any of the above embodiments.
[0056] Furthermore, the clutch 50 provided in the present application further includes the following embodiments.
[0057] In some embodiments, the circumferential side edges of the second pressing plate 552 and the positioning lug 5511 are both in contact with the side wall of the outer ring 54. Or continue to refer to Figure 11 , Figure 11 is Figure 9 an enlarged view at F. In some embodiments, a first positioning gap Δ1 and a second positioning gap Δ2 are respectively reserved between the circumferential side edges of the second pressing plate 552 and the positioning lug 5511 and the side wall of the outer ring 54. In this way, without affecting the radial positioning accuracy, a radial movement space can be provided for the second pressing plate 552 and the positioning lug 5511, improving the simplicity of structural assembly, and at the same time reducing extrusion deformation and noise.
[0058] Furthermore, in some embodiments, the value range of the first positioning gap Δ1 is less than or equal to 0.2 mm. Optionally, in some embodiments, the first positioning gap Δ1 can be 0.2 mm; in some embodiments, the first positioning gap Δ1 can be 0.1 mm.
[0059] In some embodiments, the value range of the second positioning gap Δ2 is less than or equal to 1 mm. Optionally, in some embodiments, the second positioning gap Δ2 can be 1 mm; in some embodiments, the second positioning gap Δ2 can be 0.5 mm.
[0060] In some embodiments, the engine provided in the present application includes the clutch 50 of any of the above embodiments.
[0061] The technical features of the above-described embodiments can be combined arbitrarily. For the sake of brevity of description, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, it should be considered to be within the scope described in this specification.
[0062] The above-described embodiments only represent several implementation manners of the present application. The description is relatively specific and detailed, but it should not be construed as a limitation on the scope of the patent application. It should be noted that for those of ordinary skill in the art, without departing from the concept of the present application, several deformations and improvements can still be made, and these all belong to the protection scope of the present application. Therefore, the protection scope of the patent of the present application shall be subject to the appended claims.
Claims
1. A clutch positioning mechanism, characterized in that: The clutch positioning mechanism includes a retaining frame, a first pressure plate and a second pressure plate, the retaining frame has evenly distributed mounting portions along its circumference, the mounting portions are used to mount the wedge block of the clutch, the first pressure plate and the second pressure plate are used to respectively press against the axial sides of the wedge block, the first pressure plate has at least two clamping tongues and at least two positioning tongues evenly distributed along its circumference, the radial distribution diameter of the positioning tongue is larger than the radial distribution diameter of the clamping tongue, and in the axial direction, the positioning tongue and the clamping tongue are staggered with each other and form a compression spacing, and the clamping tongue can be compressed and deformed axially relative to the positioning tongue within the compression spacing.
2. The clutch positioning mechanism according to claim 1, characterized in that: The radial direction of the pressing tongue deviates toward the side of the first pressure plate used to press the wedge block, so that the radial direction of the pressing tongue forms a deviation angle with the radial direction of the positioning tongue.
3. The clutch positioning mechanism according to claim 1, characterized in that: In a circumferential direction around the central axis of the first pressing plate, the length of the positioning tongue is greater than the length of the pressing tongue.
4. The clutch positioning mechanism according to claim 1, characterized in that: The positioning tongues and the pressing tongues have the same number and are staggeredly distributed in the circumferential direction of the first pressing plate around the central axis.
5. The clutch positioning mechanism according to claim 1, characterized in that: The retaining frame is rotationally symmetrical about the center and is in a square wave shape along its extending direction.
6. A clutch, comprising the clutch positioning mechanism according to any one of claims 1 to 5, characterized in that: The clutch also includes at least two wedges, an inner ring, an outer ring and a flywheel, the wedge being clamped in the mounting portion, the first pressure plate and the second pressure plate respectively pressing against the axial sides of the wedge, the outer ring being sleeved on the inner ring, the wedge and the retaining frame being clamped between the inner ring and the outer ring, the circumferential sides of the second pressure plate and the positioning tongue being clamped against the side wall of the outer ring, the outer ring being provided with an abutting annular surface, the clamping tongue pressing against the abutting annular surface, the flywheel and the outer ring being fixedly connected to each other along the axial direction, so that the flywheel presses against the positioning tongue along the axial direction, and the clamping tongue is compressed and deformed along the axial direction.
7. The clutch according to claim 6, characterized in that: The circumferential sides of the second pressure plate and the positioning tongue are in contact with the side walls of the outer ring; or, the circumferential sides of the second pressure plate and the positioning tongue and the side walls of the outer ring are respectively provided with a first positioning gap and a second positioning gap.
8. The clutch according to claim 6, characterized in that: A first positioning gap is reserved between the second pressing plate and the side wall of the outer ring, and a value range of the first positioning gap is less than or equal to 0.2 mm.
9. The clutch according to claim 6, characterized in that: A second positioning gap is reserved between the circumferential side edge of the positioning tongue and the side wall of the outer ring, and the value range of the second positioning gap is less than or equal to 1 mm.
10. An engine comprising the clutch according to any one of claims 6 to 9, characterized in that: The engine further comprises a motor, an idler wheel and an output crankshaft, wherein the motor is drivingly connected to the idler wheel, the idler wheel is drivingly connected to the inner ring, and the output crankshaft is drivingly connected to the inner ring.