Overrun clutch based on worm gear and worm

Abstract

The invention provides an overrun clutch based on a worm gear and a worm. According to the technical scheme, the overrun clutch comprises the worm gear and the worm, and a backlash is reserved between the worm gear and the worm; and the fixed shaft gear transmission mechanism with pretightening force is connected between the worm gear and the worm and can be used for realizing reverse driving and eliminating a transmission gap between the worm gear and the worm. By means of the worm gear, the worm and the fixed shaft gear transmission mechanism with the pretightening force, high-load transmission of the overrun clutch is achieved, and meanwhile the transmission precision is improved.

Description

Technical Field

[0001] This invention relates to the field of mechanical transmission system technology, and specifically to an overrunning clutch. Background Technology

[0002] Overrunning clutches are fundamental components in mechanical transmission systems. They are mainly classified into three basic types: ratchet, roller, and wedge. They are widely used in the automotive, aerospace, automated machinery, and energy industries.

[0003] Existing ratchet-type overrunning clutches, due to their rigid meshing structure, require a pre-existing meshing clearance, resulting in idle travel and low transmission accuracy.

[0004] Existing wedge-type and roller-type overrunning clutches utilize the wedge effect and the squeezing and releasing action of rollers, respectively, to achieve their functions. These two operating methods result in low load capacity, excessive stress at the contact points with the wedge or roller, and a tendency to cause contact fatigue and pitting. They also impose high requirements on manufacturing precision and material wear resistance.

[0005] Therefore, there is a need in the art for a new overrunning clutch solution that can overcome the disadvantages of at least one of the above. Summary of the Invention

[0006] Technical problems to be solved: The main objective of this invention is to propose an overrunning clutch based on a worm gear, in order to solve the shortcomings of existing ratchet-type overrunning clutches, such as idle travel and low precision, as well as the small load capacity of wedge-type and roller-type overrunning clutches.

[0007] Technical solution:

[0008] In this application, the term "reverse drive" specifically refers to a transmission mode in which a worm gear, as the driving element, drives another mechanism to drive the worm to rotate around its own axis according to the transmission ratio and transmission direction of the worm gear to the worm.

[0009] A worm gear-based overrunning clutch, characterized in that it comprises: A worm gear and a worm, with a side clearance between the worm gear and the worm; A fixed-axis gear transmission mechanism with preload is connected between the worm gear and the worm and can be used to achieve reverse drive and eliminate transmission backlash between the worm gear and the worm.

[0010] Optionally, the preloaded fixed-axis gear transmission mechanism is preloaded by a spring.

[0011] Optionally, the spring in the preloaded fixed-axis gear transmission mechanism is a cylindrical helical spring, a spiral spring, or a torsion spring.

[0012] Optionally, the preloaded fixed-axis gear transmission mechanism is preloaded by an elastic material.

[0013] Optionally, the elastic material in the preloaded fixed-axis gear transmission mechanism is elastic rubber or elastic plastic.

[0014] Optionally, the transmission part of the preloaded fixed-axis gear transmission mechanism is a combination of bevel gear pairs and cylindrical gear pairs.

[0015] Furthermore, the preloaded fixed-axis gear transmission mechanism includes a spring-loaded reversing mechanism to change the direction of the preload, thereby enabling the overrunning clutch to change the direction of force transmission.

[0016] Optionally, the elastic reversing mechanism is a knob with an eccentric connection structure.

[0017] Optionally, the elastic reversing mechanism is a paddle with a bearing.

[0018] Furthermore, the preloaded fixed-axis gear transmission mechanism includes a limit structure to restrict the stroke of the preload, thereby preventing the worm gear from locking up during the overrun stage.

[0019] Optionally, the limiting structure is a limiting block.

[0020] Furthermore, there may be one or more worm gears, and increasing the number of worm gears can increase the load capacity of this overrunning clutch.

[0021] Beneficial effects:

[0022] Compared with existing ratchet-type overrunning clutches, this invention utilizes the backlash elimination function of a preloaded fixed-axis gear transmission mechanism, ensuring that the worm gear and worm are in contact during both the overrunning and power transmission stages under normal operating conditions. This greatly avoids backlash in the transmission and improves transmission accuracy.

[0023] Compared with existing wedge-type and roller-type overrunning clutches, this invention utilizes a worm gear structure, and multiple worms can cooperate with a worm wheel, making the load capacity of this invention stronger than that of wedge-type and roller-type overrunning clutches.

[0024] The present invention achieves reversing in a very simple way, and can easily select between reversible and non-reversible schemes, thereby expanding the scope of application. Attached Figure Description

[0025] In all the following figures, the same reference numerals denote the same or similar elements. The figures are only schematic diagrams for clear illustration, and their scale, dimensions and other details are not intended to limit the actual implementation of the present invention.

[0026] Figure 1This is an exploded view of Embodiment 1 of the present invention.

[0027] Figure 2 This is a cross-sectional view of Embodiment 1 of the present invention.

[0028] Figure 3 This is a schematic diagram of the worm gear structure according to Embodiment 1 of the present invention.

[0029] Figure 4 This is a cross-sectional view of a fixed-axis gear transmission mechanism with preload in Embodiment 1 of the present invention.

[0030] Figure 5 This is a partial exploded view of the fixed-axis gear transmission mechanism with preload in Embodiment 1 of the present invention.

[0031] Figure 6 This is an exploded view of Embodiment 2 of the present invention.

[0032] Figure 7 This is a schematic diagram of the structure of Embodiment 2 of the present invention.

[0033] Figure 8 This is an exploded view of Embodiment 3 of the present invention.

[0034] Figure 9 This is a schematic diagram of the structure of Embodiment 3 of the present invention.

[0035] Figure 10 This is a partial exploded view of Embodiment 3 of the present invention.

[0036] Figure 11 This is a schematic diagram of the structure of Embodiment 4 of the present invention.

[0037] Figure 12 This is an exploded view of Embodiment 4 of the present invention.

[0038] Reference numerals: 1-worm gear; 2-worm; 3-fixed-axis gear transmission mechanism with preload; 4-input mechanism; 5-output mechanism; 51-center bearing; 52-edge bearing; 31-fixed ring; 32-knob with eccentric shaft; 33-scroll spring; 34-helical gear; 341-elliptical ring limit stop; 35-helical gear-bevel gear composite shaft; 36-bevel gear; 37-drive shaft; 38-anti-disengagement snap ring. 4A - Splined shaft; 5A - Single output mechanism; 32A - Paddle with bearing; 321A - Circular limit stop; 33A - Cylindrical helical spring; 34A - Sliding helical gear; 39A - Limit circlip. 1B - Right-hand worm gear; 2B - Right-hand worm; 21B - Semi-circular limit stop; 4B - Splined shaft spur gear compound input mechanism; 5B - Triple output mechanism; 33B - Torsion spring; 35B - Spur gear bevel gear compound shaft; 36B - Bevel gear with limit structure; 361B - Sector-shaped limit stop. 1C - Left-handed worm gear; 2C - Left-handed worm; 4C - Splined shaft bevel gear compound input mechanism; 5C - Single-sided output mechanism; 33C - Sector-shaped elastic rubber block; 35C - Small bevel gear and large spur gear compound shaft; 36C - Spur gear with irregular hole. Detailed Implementation Plan

[0039] To make the objectives, technical solutions, and advantages of the present invention clearer, the technical solutions in the embodiments of the present invention will be described in detail below with reference to the accompanying drawings. It should be understood that these descriptions are intended to illustrate the present invention and not to limit its scope of protection.

[0040] Example 1:

[0041] Please see Figure 1 , Figure 2 , Figure 3 This embodiment provides an overrunning clutch based on a worm gear, the core innovation of which lies in: mainly including a worm gear 1, a worm 2, and a fixed-axis gear transmission mechanism 3 with preload. Worm gear 1 and worm 2 can form a worm gear pair with backlash. The transmission ratio and transmission direction of the preloaded fixed-axis gear transmission mechanism 3 allow worm gear 1 and worm 2 connected to this mechanism to achieve reverse driving through this mechanism. A preloaded fixed-axis gear transmission mechanism 3 is configured between the worm gear 1 and the worm 2 for transmission. The preload in the preloaded fixed-axis gear transmission mechanism 3 causes the worm 2 to rotate around its own axis until it contacts one side of the tooth wall of the worm gear 1 and stops, maintaining a certain preload. A gap is then left between the other side of the tooth wall of the same tooth groove and the worm 2. Because of the presence of the preload, the reverse drive between the worm gear 1 and the worm 2 can only be achieved through the preloaded fixed-axis gear transmission mechanism 3 when the driving force on the worm gear 1 opposes the force exerted by the preload on the worm gear 1. When the externally input rotational power drives the worm wheel 1 to rotate, and the direction is consistent with the direction of the preload force acting on the worm wheel 1, the rotation direction of the worm wheel 1 is towards the side in contact with the worm 2. The externally input power will then drive the worm wheel 1 to drive the worm 2, instead of driving the worm 2 through the fixed-axis gear transmission mechanism 3 with preload. Furthermore, because the high friction angle between the worm wheel 1 and the worm 2 locks the worm 2 to rotate around its own axis, it drives the worm 2 to rotate around the worm wheel 1 and output rotational power, thus realizing the transmission process of this embodiment. When the externally input rotational power drives the worm wheel 1 to rotate in the opposite direction to the preload force acting on the worm wheel 1, the rotation direction of the worm wheel 1 is towards the side with a gap between it and the worm 2. The fixed-axis gear transmission mechanism 3 with preload will, due to the preload force and the gap between the worm wheel 1 and the worm 3, drive the worm wheel 2 to rotate around its own axis before the worm wheel 1, achieving reverse drive and thus realizing the overtaking process of this embodiment. Therefore, changing the direction of the preload force can change the transmission direction of this embodiment. Throughout the process, when the preloaded fixed-axis gear transmission mechanism 3 does not change the direction of the preload, the worm 2 always contacts one side of the tooth wall of the worm wheel 1, whether in the overtaking stage or the force transmission stage, thus achieving that no idle stroke is formed when switching between the overtaking and force transmission stages in this embodiment.

[0042] Please see Figure 1 This embodiment includes: a worm gear 1, a worm 2, a fixed-axis gear transmission mechanism with preload 3, an input mechanism 4, and an output mechanism 5.

[0043] Please see Figure 2 The worm gear 1 has 13 teeth and is integrally formed with the input mechanism 4. The worm gear 1 also has an integrally formed shaft connected to the central bearing 8. The worm gear 1 is rotatably connected to the output mechanism 5 through the central bearing 51. The worm gear 1 is used to lock with the worm 2 during the force transmission stage in this embodiment, thereby achieving the transmission purpose.

[0044] Please see Figure 3 The worm 2 is a single-headed worm and has a keyway that can be coaxially and fixedly connected to the transmission shaft 37. It is combined with the worm wheel 1 to form a worm wheel and worm pair with backlash. In this embodiment, there are two symmetrically arranged worms 2. Obviously, it can also be configured as one or more. The more worms 2 that cooperate with the worm wheel 1, the greater the load capacity of the transmission.

[0045] Please see Figure 2 , Figure 4 , Figure 5 The preloaded fixed-axis gear transmission mechanism 3 consists of a fixed ring 31, a knob 32 with an eccentric shaft, a spiral spring 33, a helical gear 34, a helical-bevel gear composite shaft 35, a bevel gear 36, a transmission shaft 37, and an anti-disengagement snap ring 38. In this embodiment, the composite gear 35, the bevel gear 36, the transmission shaft 37, and the anti-disengagement snap ring 38 are all symmetrically arranged in two configurations to cooperate with the worm gear 2. The retaining ring 31 consists of a spline sleeve and a knob mounting base with two positioning grooves. The spline sleeve is fixedly connected to the input mechanism 4, and the knob mounting base with two positioning grooves is used to assemble the reversing knob 32. The knob 32 with an eccentric shaft consists of a knob cap, a knob spindle equipped with a spring plunger, and an eccentric shaft, which is fitted into the inner ring of a spiral spring 33. The spiral spring 33 has an inner ring and an outer ring. When the spiral spring 33 is not under force, the inner ring and the outer ring are concentric, and the outer ring is embedded in the groove of the helical gear 34. The helical gear 34 has 91 teeth and is provided with a central shaft hole, a spring mounting hole, and an elliptical annular stop block 341 whose major axis points to the center of the helical gear 34. The helical gear 34 is coaxially hinged to the input mechanism 4 through the central shaft hole. The helical gear and bevel gear composite shaft 35 has a helical gear end with 7 teeth and a bevel gear end with 11 teeth. The helical gear end meshes with a helical gear 34, and the bevel gear end meshes with a bevel gear 36. An edge bearing 9 is assembled between the two ends. The bevel gear 36 has 11 teeth and a key with an opening on its shaft, and is fixedly connected to the drive shaft 37 via a keyway. The drive shaft 37 consists of a large shaft and a small shaft. The large shaft has a keyway that mates with the worm gear 2, and the small shaft has a keyway that mates with the bevel gear 36, as well as a circlip groove for mounting the anti-disengagement circlip 38. With this configuration, the fixed ring 31 will rotate synchronously with the input mechanism 4. The knob 32 with the eccentric shaft can be mounted on the fixed ring 31, and the spring plunger on the knob 32 with the eccentric shaft can be inserted into the positioning groove of the fixed ring 31, so that the knob 32 with the eccentric shaft can maintain a fixed angle. Then, the eccentric shaft in the knob 32 with the eccentric shaft will drive the inner ring of the spiral spring 33 to generate elastic force, thereby generating a preload between the knob 32 with the eccentric shaft and the helical gear 34. This preload is then transmitted through the helical gear bevel gear composite shaft 35, bevel gear 36, and transmission shaft 37, causing the worm 2 to rotate around its own axis until it contacts the tooth wall of the worm wheel 1, thereby eliminating the transmission gap between the worm wheel 1 and the worm 2. Maintaining preload in the opposite direction, the elliptical annular stop block 341 on the helical gear 34 is designed to prevent jamming when the helical gear 34 rotates in the opposite direction of the preload, causing the worm 2 to move beyond the backlash between it and the worm wheel 1 and lock into contact with the other tooth wall of the same tooth groove of the worm wheel 1. The elliptical annular stop block 341 is elliptical rather than circular because, while ensuring the rotation space of the knob 32 with the eccentric shaft, it is also necessary for the elliptical annular stop block 341 to still achieve the limiting effect after the knob 32 with the eccentric shaft rotates, without being affected by the backlash between the worm wheel 1 and the worm 2. This enables the fixed-axis gear transmission mechanism 3 with preload to be used for reverse drive between the worm gear 1 and worm 2. The direction of its preload can be changed, and its preload can be used to eliminate the transmission gap between the worm gear and worm. The elliptical ring limit stop 341 is used to prevent the worm gear 1 and worm 2 from locking up during the overrun stage.

[0046] As explained above, it is obvious that the spiral spring 33 can be completely replaced by a disc-shaped elastic rubber block or an elastic plastic block with a central hole.

[0047] Please see Figure 1 , Figure 2 The output mechanism 6 consists of a splined shaft and a housing, as well as a central bearing 8 and an edge bearing 9 that can be fixed on the housing. It is rotatably connected to the transmission shaft 36 through a hole in the housing. The worm gear 2 is restricted from sliding along its own axis by the inner wall of the housing. The output mechanism 6 is used to fix the relative position of its connected parts and to output rotational power externally driven by the worm gear 2.

[0048] Example 2:

[0049] Figure 6 , Figure 7 This illustration shows a second embodiment of the present invention. The main difference from the first embodiment is that the worm gear 2 is reduced to one, the output mechanism 5 is replaced with a single-stage output mechanism 5A adapted to a single worm gear, and some structures of the fixed-axis gear transmission mechanism 3 with preload are modified, including: a bearing-loaded paddle 32A, a cylindrical helical spring 33A, a sliding helical gear 34A, and a limiting snap ring 39A. The remaining parts are the same as in the first embodiment. The paddle 32A with bearing is mainly composed of a bearing. The outer ring of the bearing is integrally formed with the adjustment paddle. The function of the adjustment paddle is to drive the bearing to move axially. Circular limit blocks 321A are also arranged on both sides of the inner ring of the bearing. The function of the paddle 32A with bearing is the same as that of the knob 32 with eccentric shaft in Embodiment 1, both used to change the direction of preload. A cylindrical helical spring 33A is configured to fit on the annular limiting block 321A of the bearing-bearing paddle 32A, with one on each side. The size of the cylindrical helical spring 33A is configured so that it will not contact any part of the bearing-bearing paddle 32A other than the inner ring of the bearing and the annular limiting block 321A. The function of the cylindrical helical spring 33A is the same as that of the spiral spring 33 in Embodiment 1, which is to provide a source of preload force. The sliding helical gear 34A is integrally formed from a helical gear and a sliding spline sleeve. The sliding spline sleeve enables the sliding helical gear 34A to slide axially and rotate synchronously on the spline shaft 4A. The sliding spline sleeve has a retaining groove for installing a retaining spring 39A. The outer ring of the sliding spline sleeve allows the inner ring of the bearing-bearing paddle 32A to be fitted on it, enabling axial movement.

[0050] In this embodiment, the bearing-bearing paddle 32A and the cylindrical helical springs 33A arranged on both sides are both fitted onto the outer ring of the sliding spline sleeve of the sliding helical gear 34A and locked with a limiting snap ring 39A. The limiting snap ring 39A restricts the axial movement distance of the bearing-bearing paddle 32A on the sliding helical gear 34A. The bearing-bearing paddle 32A, by compressing the cylindrical helical springs 33A, drives the sliding helical gear 34A to slide axially on the spline shaft 4A. Because of the helical gear on the sliding helical gear 34A, its axial movement will also drive the helical gear meshing with it to rotate, realizing transmission with preload. The contact between the annular limiting block 321A and the sliding helical gear 34A and the limiting snap ring 39A limits the distance of the preload.

[0051] As explained above, it is obvious that the cylindrical helical spring 33A can be completely replaced by a cylindrical elastic rubber or cylindrical elastic plastic.

[0052] The advantage of this embodiment compared to embodiment one is that the reversing is achieved through the bearing design in the bearing-bearing paddle 32A and the axial movement, allowing the reversing to occur during the operation of this embodiment.

[0053] Example 3:

[0054] Please see Figure 8 , Figure 9 The main difference between this embodiment and Embodiment 1 is that the left-handed worm gear 1 and worm 2 are replaced with a 9-tooth right-handed worm gear 1B and three right-handed worms 2B. The output mechanism 5 is changed to a triple output mechanism 5B adapted to the three worms. The input mechanism 4 is changed to a splined shaft spur gear compound input mechanism 4B, wherein the spur gear has 45 teeth. The structure of the fixed-axis gear transmission mechanism 3 with preload is changed, including: a spur gear bevel gear compound shaft 35B, a bevel gear 36B with a limiting structure, and a torsion spring 33B. The rest is the same as in Embodiment 1. The right-hand worm gear 2B has a circular baffle that is coaxial with and integrally formed at one end, from which a connecting shaft extends. At the end of the connecting shaft, there is a semi-circular limiting block 21B and a small shaft coaxial with it. The small shaft also has a torsion spring fixing hole. Please see Figure 10 The spur gear and bevel gear composite shaft 35B has a 7-tooth spur gear end and a 12-tooth bevel gear end. The bevel gear end is also equipped with a small shaft for mounting in the bearing of the triple output mechanism 5B. The spur gear end meshes with a 45-tooth spur gear in the splined shaft spur gear composite input mechanism 4B, and the bevel gear end meshes with a 10-tooth bevel gear in the bevel gear 36B with a limiting structure. The bevel gear 36B with a limiting structure has a central opening for rotatable connection to the small shaft of the right-hand worm gear 2B. The limiting structure is a fan-shaped limiting block 361B, which can cooperate with the semi-circular limiting block 21B on the right-hand worm gear 2B to limit the rotation angle of the bevel gear 36B on the right-hand worm gear 2B. A torsion spring fixing hole is also provided on the bevel gear side of the limiting structure bevel gear 36B. The two ends of the torsion spring 33B are connected to the torsion spring fixing holes on the bevel gear 36B with the limiting structure and the right-hand worm gear 2B, respectively. The function of the torsion spring 33B is the same as that of the spiral spring 33 in Embodiment 1, which is to provide a source of preload.

[0055] In this embodiment, a torsion spring 33B is arranged between the right-hand worm gear 2B and the bevel gear 36B with a limiting structure to generate a preload. A semi-circular limiting block 21B and a sector-shaped limiting block 361B are used to limit the rotation angle of the bevel gear 36B with the limiting structure relative to the right-hand worm gear 2B in the opposite direction to the preload, thereby limiting the distance of the preload. This embodiment eliminates the elastic force reversing mechanism, so that this embodiment can only transmit in one direction.

[0056] The advantages of this embodiment compared to Embodiment 1 are: the number of worm gears is increased, thereby increasing the load capacity, and the elastic force reversal mechanism is eliminated, thereby reducing the system complexity.

[0057] Example 4:

[0058] Please see Figure 11 , Figure 12 The main difference between this embodiment and Embodiment 1 is that the worm gear 1 and worm 2 are replaced with a 9-tooth left-hand worm gear 1C and a left-hand worm 2C; the output mechanism 5 is replaced with a single-sided output mechanism 5C that can adapt to a single worm and connect to a small bevel gear and a large spur gear composite shaft 35C; the input mechanism 4 is replaced with a splined shaft bevel gear composite input mechanism 4C, wherein the bevel gear has 27 teeth; and the structure of the fixed-axis gear transmission mechanism 3 with preload is changed, including: a small bevel gear and a large spur gear composite shaft 35C, a spur gear 36C with a special-shaped hole, and a sector-shaped elastic rubber block 33C. The rest of the parts are the same as in Embodiment 1. The left-hand worm gear 2C has a circular baffle that is coaxial with and integrally formed at one end, from which a connecting shaft extends. At the end of the connecting shaft is a non-circular shaft, which is used to rotatably connect with the spur gear 36C with a non-circular hole and to limit the rotation angle. The composite shaft 35C, consisting of a small bevel gear and a large spur gear, has a 9-tooth bevel gear end and a 27-tooth spur gear end. The spur gear end is also equipped with a small shaft for connection to the single-sided output mechanism 5C via bearings. The bevel gear end meshes with the 27-tooth bevel gear in the splined shaft bevel gear composite input mechanism 4C, and the spur gear end meshes with a 9-tooth spur gear 36C with a shaped bore. The spur gear 36C with irregular holes has an irregular hole in the middle and is connected to the irregular shaft of the left-hand worm gear 2C. The irregular hole has rotation space on both sides of the irregular shaft, and a fan-shaped elastic rubber block 33C is arranged on one side to provide preload.

[0059] In this embodiment, the gear combination structure of the fixed-axis gear transmission mechanism 3 with preload in Embodiment 1 is changed. A sector-shaped elastic rubber block 33C is used to provide preload, and the elastic force reversing mechanism and limiting structure are eliminated, so that this embodiment can only transmit in one direction and can only operate under stable working conditions.

[0060] Through the above four embodiments, it can be seen that the limiting structure for restricting the preload in the preload-bearing fixed-axis gear transmission mechanism 3 can be a limiting block of various shapes, as long as it prevents the worm from contacting the other tooth wall in the same tooth groove on the worm wheel in advance during the overshoot stage. It is also explained that the preload-bearing fixed-axis gear transmission mechanism 3 can produce various structural changes due to the spiral orientation and number of worms connected to it, the configuration position and type of springs, the type of transmission gears used, and the presence and type of elastic reversing mechanism. Therefore, as long as the transmission ratio and transmission direction of the preload-bearing fixed-axis gear transmission mechanism 3 meet the requirements of achieving reverse drive between the worm wheel and worm connected to it, and using the preload to eliminate the transmission gap between the worm wheel and worm, the effect of the preload-bearing fixed-axis gear transmission mechanism 3 can be achieved, solving the problems in the prior art.

[0061] The above description is merely a specific embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the scope of the technology disclosed in the present invention should be included within the scope of protection of the present invention. Therefore, the scope of protection of the present invention shall be determined by the scope of the claims.

Claims

1. A worm gear-based overrunning clutch, characterized in that, include: Worm wheel (1) and worm (2), with a side clearance between the worm wheel (1) and the worm (2); A fixed-axis gear transmission mechanism (3) with preload is connected between the worm wheel (1) and the worm (2) and can be used to achieve reverse drive and eliminate transmission gap between the worm wheel (1) and the worm (2).

2. The overrunning clutch based on a worm gear according to claim 1, characterized in that, The preloaded fixed-axis gear transmission mechanism (3) is preloaded by a spring.

3. The overrunning clutch based on a worm gear according to claim 2, characterized in that, The spring is a cylindrical helical spring, a spiral spring, or a torsion spring.

4. The overrunning clutch based on a worm gear according to claim 1, characterized in that, The fixed-axis gear transmission mechanism (3) with preload is driven by a combination of bevel gear pairs and cylindrical gear pairs.

5. The overrunning clutch based on a worm gear according to claim 1, characterized in that, The fixed-axis gear transmission mechanism (3) with preload is also equipped with a spring force reversing mechanism that can change the direction of the preload.

6. The overrunning clutch based on a worm gear according to claim 5, characterized in that, The elastic reversing mechanism is a knob (32) with an eccentric shaft.

7. A worm gear-based overrunning clutch according to claim 5, characterized in that, The elastic reversing mechanism is a paddle (32A) with a bearing.

8. A worm gear-based overrunning clutch according to claim 1 or 5, characterized in that, The fixed-axis gear transmission mechanism (3) with preload is also equipped with a limiting structure that can limit the stroke of the preload.

9. A worm gear-based overrunning clutch according to claim 7, characterized in that, The limiting structure is a limiting block.

10. A worm gear-based overrunning clutch according to claim 1, 5, or 8, characterized in that... The worm gear (2) is configured as one or more.

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