A shuttle speed change mechanism

Abstract

The present invention relates to the field of cableway transportation equipment, and specifically discloses a shuttle speed change mechanism, including a shift lever, and a first gear and a second gear sleeved on the shift lever and having different numbers of teeth; the outer periphery of the shift lever is axially provided with a gear set located between the first gear and the second gear, the interior of the first gear is provided with a first tooth groove that cooperates and plugs with the first end of the gear set, and the interior of the second gear is provided with a second tooth groove that cooperates and plugs with the second end of the gear set; the shift lever moves axially back and forth to allow the first end of the gear set to be plugged into the first tooth groove or the second end of the gear set to be plugged into the second tooth groove. The shuttle speed change mechanism of the present invention has a simple and practical structure, has a multi-gear structure, can realize speed control of the shuttle, is conducive to adapting to different terrain changes, and improves the safety of shuttle operation.

Description

Technical Field

[0001] The invention relates to the technical field of cableway transportation equipment, in particular to a shuttle speed changing mechanism. Background Art

[0002] Using ropeways to transport goods is a traditional logistics transportation method, and it is still used in some occasions today. Using shuttles to transport goods on ropeways is an improvement on the traditional ropeway system, which helps to transport goods to different destinations more quickly and efficiently. The current shuttles are usually composed of a control component, a drive mechanism, and a boom mechanism connecting the control component and the drive mechanism, wherein the control component can control the drive mechanism so that the drive mechanism drives the shuttle to travel along the ropeway.

[0003] Unlike traditional technologies, cableways are no longer just single straight cableways. Cableways need to turn in different terrains. However, due to the limitations of the shuttle drive mechanism, currently commonly used shuttles can only run on the cableway at a constant speed and cannot change speed when turning. Due to the influence of centrifugal force, if the speed of the shuttle does not change when turning, it is easy to derail, which may lead to unnecessary dangers and have a great impact on the overall operating cost and work efficiency of the cableway system. Therefore, in order to improve the operating safety factor of the shuttle, it is urgent to design a shuttle with variable speed, reduce the speed when turning or going downhill to reduce the operating risk, and appropriately increase the speed when going uphill to improve the shuttle's climbing ability, so as to avoid stagnation or retreat due to heavy loads, so as to adapt to the operating requirements of different terrains.

[0004] In summary, the shuttle must have a transmission mechanism with gear shifting to better utilize different speeds to adapt to different terrains. However, most of the existing gear shifting mechanisms are used for cars, motorcycles, electric vehicles, etc., and their size and weight exceed the design requirements of the shuttle. Summary of the invention

[0005] In order to solve the problems in the above-mentioned background technology, the purpose of the present invention is to provide a shuttle speed change mechanism, which has a simple and practical structure, a multi-gear structure, can realize the speed change control of the shuttle, is conducive to adapting to different terrain changes, and improves the safety of shuttle operation.

[0006] Based on this, the present invention provides a shuttle speed change mechanism, which

[0007] The invention comprises a shift lever, and a first gear and a second gear sleeved on the shift lever and having different numbers of teeth; a gear set located between the first gear and the second gear is axially arranged on the outer circumference of the shift lever, a first tooth groove is arranged inside the first gear to be plugged with the first end of the tooth set, and a second tooth groove is arranged inside the second gear to be plugged with the second end of the tooth set;

[0008] The shift lever moves axially back and forth so that the first end of the tooth set is inserted into the first tooth groove or the second end of the tooth set is inserted into the second tooth groove;

[0009] The first gear has a first conical inner wall opening toward the second gear, and the second gear has a second conical inner wall opening toward the first gear; the first tooth groove is arranged on the first conical inner wall, and the second tooth groove is arranged on the second conical inner wall; a storage space is formed between the first conical inner wall and the second conical inner wall, and the tooth group is located in the storage space.

[0010] Furthermore, the angle between two generatrixes of the axial section of the first tapered inner wall is in the range of 15-90 degrees, and the angle between two generatrixes of the axial section of the second tapered inner wall is in the range of 15-90 degrees.

[0011] Furthermore, the first conical inner wall, the second conical inner wall and the shift lever are coaxially arranged.

[0012] Further, a diameter of the opening of the first tapered inner wall is the same as a diameter of the opening of the second tapered inner wall.

[0013] Furthermore, a release position is provided on the moving path of the tooth group; when the tooth group is located at the release position in the receiving space, the tooth group is separated from the first tooth groove, and the tooth group is separated from the second tooth groove.

[0014] Further, the position where the tooth group is meshed with the first tooth groove is the first position, and the position where the tooth group is meshed with the second tooth groove is the second position; the distance that the tooth group moves from the release position to the first position is the first distance, and the distance that the tooth group moves from the release position to the second position is the second distance; the first distance is equal to the second distance; the ratio of the first distance to the second distance is: 0.5~2.

[0015] Further, the tooth set includes a first helical tooth and a second helical tooth which are axially arranged and inclined in opposite directions, the first tooth groove is used for mating and plugging with the first helical tooth, and the second tooth groove is used for mating and plugging with the second helical tooth.

[0016] Furthermore, the shuttle speed change mechanism also includes a thrust bearing sleeved on the shift lever and arranged between the first gear and the second gear.

[0017] Furthermore, an extension sleeve is provided on one end of the first gear and the second gear close to the thrust bearing, and the thrust bearing is sleeved on the extension sleeve.

[0018] Further, the inclination angle α of the first oblique teeth is in the range of 3-30°, and the inclination angle α of the second oblique teeth is in the range of 3-30°.

[0019] Compared with the prior art, the beneficial effects of the present invention are:

[0020] The shuttle speed change mechanism of the present invention comprises a shift lever, a first gear and a second gear sleeved on the shift lever, wherein a first tooth groove is provided inside the first gear and a second tooth groove is provided inside the second gear, and a tooth group is axially provided on the outer periphery of the shift lever and the tooth group is axially moved between the first gear and the second gear, and the first end of the tooth group is inserted into the first tooth groove after the shift lever is pushed forward, or the second end of the tooth group is inserted into the second tooth groove after the shift lever is moved backward, so that when the first end of the tooth group is inserted into the first tooth groove to achieve meshing, the second end of the tooth group is disengaged from the second tooth groove, so that the first gear and the corresponding external transmission component are transmitted; when the second end of the tooth group is inserted into the second tooth groove to achieve meshing, the first end of the tooth group is disengaged from the first tooth groove, so that the second gear and the corresponding external transmission component are transmitted; when the second end of the tooth group is inserted into the second tooth groove to achieve meshing, the first end of the tooth group is disengaged from the first tooth groove, so that the second gear and the corresponding external transmission component are transmitted. The external transmission component is used for transmission. Since the number of teeth of the first gear and the second gear is different, transmission is performed by switching the first gear and the second gear, that is, the engagement and loosening states of the two ends of the tooth group of the shift lever and the tooth grooves in the two gears are utilized to achieve multiple gears to control the advancement of the shuttle, thereby realizing the speed control of the shuttle. The speed change mechanism has multiple gears, which can realize the speed control of the shuttle, and is conducive to adapting to different terrain changes, thereby improving the operating safety performance of the shuttle. At the same time, the shift speed mechanism greatly reduces the occupied volume of the traditional shift box, reduces the occupied volume and weight to a minimum, and integrates the transmission shaft and the shift lever into an integrated design, thereby realizing a small-volume multi-gear speed change function, which meets the overall design requirements of the shuttle. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] Figure 1 is a schematic diagram of a shuttle speed change mechanism provided in Embodiment 1 of the present invention;

[0022] Figure 2 is a three-dimensional diagram of a shuttle speed change mechanism provided by the first embodiment of the present invention;

[0023] Figure 3 is a schematic diagram of a tooth profile development surface of a gear set on a shift lever provided in Embodiment 1 of the present invention;

[0024] Figure 4 is a schematic diagram of a shift lever provided in Embodiment 2 of the present invention;

[0025] Figure 5 is a schematic diagram of the tooth profile development surface of the upper tooth group of the shift lever provided in the second embodiment of the present invention;

[0026] Figure 6 is a schematic diagram of a first gear provided in Embodiment 2 of the present invention;

[0027] Figure 7 is a schematic diagram of a second gear provided in Embodiment 2 of the present invention;

[0028] Figure 8 is a diagram of the use state of the shift lever when it is pushed forward according to the second embodiment of the present invention;

[0029] Fig. 9 This is a diagram of the shift lever in the second embodiment of the present invention when it is in use and moves backward.

[0030] Among them, 1. shift lever; 2. first gear; 21. first tooth groove; 22. first extension sleeve; 3. second gear; 31. second tooth groove; 32. second extension sleeve; 4. gear set; 41. first helical tooth; 42. second helical tooth; 5. thrust bearing; 6. drive motor; 7. push-pull motor; 71. connecting sleeve. DETAILED DESCRIPTION

[0031] The specific implementation of the present invention is further described in detail below in conjunction with the accompanying drawings and examples. The following examples are used to illustrate the present invention, but are not intended to limit the scope of the present invention.

[0032] In the description of the present invention, it should be noted that the terms "upper", "lower", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside" and the like indicate positions or positional relationships based on the positions or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention 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 therefore cannot be understood as a limitation on the present invention. It should be understood that the terms "first", "second", etc. are used in the present invention to describe various information, but such information should not be limited to these terms, which are only used to distinguish the same type of information from each other. For example, without departing from the scope of the present invention, the "first" information may also be referred to as the "second" information, and similarly, the "second" information may also be referred to as the "first" information.

[0033] Embodiment 1:

[0034] See also Figure 1 and Figure 2As shown, the shuttle speed change mechanism of the present invention is schematically shown, which includes a shift lever 1, a first gear 2 and a second gear 3, wherein the first gear 2 and the second gear 3 have different numbers of teeth and are sleeved on the shift lever 1, and a gear set 4 is axially provided on the outer periphery of the shift lever 1, and the gear set 4 is located between the first gear 2 and the second gear 3. It is important that a first tooth groove 21 is provided inside the first gear 2, and a second tooth groove 31 is provided inside the second gear 3, and the first tooth groove 21 is used to be connected with the first end ( Figure 1 The left end of the middle tooth group 4) is plugged in with the second tooth groove 31, and the second tooth groove 31 is used to connect with the second end ( Figure 1 The right end of the middle tooth group 4) is plugged in with the other end.

[0035] The shuttle speed change mechanism based on the above technical features is provided with a gear set 4 axially on the outer periphery of the shift lever 1, and the gear set 4 is moved axially between the first gear 2 and the second gear 3, by pushing forward (such as Figure 8 As shown, the shift lever 1 moves leftward) so that the first end of the gear set 4 is inserted into the first tooth groove 21, or moves backward (as shown Fig. 9 As shown, the shift lever 1 moves to the right) and the shift lever 1 makes the second end of the tooth set 4 inserted into the second tooth groove 31. In this way, when the first end of the tooth set 4 is inserted into the first tooth groove 21 to achieve meshing, the second end of the tooth set 4 is disengaged from the second tooth groove 31, and the first gear 2 starts to rotate, so that the first gear 2 and the corresponding external transmission component (such as a sun gear system) are transmitted; when the second end of the tooth set 4 is inserted into the second tooth groove 31 to achieve meshing, the first end of the tooth set 4 is disengaged from the first tooth groove 21, and the second gear 3 starts to rotate, so that the second gear 3 and the corresponding external transmission component are transmitted. The number of teeth of gear 2 and the second gear 3 are different. By switching the first gear 2 and the second gear 3 for transmission, the speed control of the shuttle can be realized. The speed change mechanism has a simple and practical structure, has multiple gears, can realize the speed control of the shuttle, and is conducive to adapting to different terrain changes, thereby improving the operating safety performance of the shuttle. At the same time, the shifting speed mechanism greatly reduces the occupied volume of the traditional shift box, reduces the occupied volume and weight to the minimum, and integrates the transmission shaft and the shift lever to realize the small volume and multi-gear speed change function, which meets the overall design requirements of the shuttle. In this embodiment, Figure 1As shown, the first end of the shift lever 1 is used to be connected to the driving motor 6, and the second end thereof is used to be connected to the push-pull motor 7. The push-pull motor 7 is connected to the second section of the shift lever 1 through the connecting sleeve 71. The push-pull motor 7 provides power to push the shift lever 1 forward or backward, so that the first end of the tooth group 4 on the shift lever 1 is meshed with the first tooth groove 21 or the second end of the tooth group 4 is meshed with the second tooth groove 31. The drive motor 6 then drives the shift lever 1 to rotate, thereby realizing the rotation of the first gear 2 or the rotation of the second gear 3, realizing the switching of the gear position, and then realizing the speed control of the shuttle. Of course, in other embodiments, the second end of the shift lever 1 can also be connected through a cylinder, as long as the push-pull function of the present invention can be achieved, and it will not be repeated here.

[0036] The first gear 2 has a first conical inner wall with an opening toward the second gear 3, and the second gear 3 has a second conical inner wall with an opening toward the first gear 2; the first tooth groove 21 is arranged on the first conical inner wall, and the second tooth groove 31 is arranged on the second conical inner wall; a storage space is formed between the first conical inner wall and the second conical inner wall, and the tooth group 4 is located in the storage space. In this way, the tooth group 4 is arranged in the storage space for protection, and when the tooth group 4 approaches the first tooth groove 21 on the first conical inner wall, the tooth group 4 is wrapped by the first conical inner wall to prevent the tooth group 4 from being separated from the first tooth groove 21 during the transmission process; when the tooth group 4 approaches the second tooth groove 31 on the second conical inner wall, the tooth group 4 is wrapped by the second conical inner wall to prevent the tooth group 4 from being separated from the second tooth groove 31 during the transmission process.

[0037] Specifically, Figure 1 , Figure 3 and Figure 4 As shown, the angle between the two generatrixes of the axial section of the first conical inner wall is in the range of 15-90 degrees, and the angle between the two generatrixes of the axial section of the second conical inner wall is in the range of 15-90 degrees. In this way, when the tooth set 4 approaches the first tooth groove 21 on the first conical inner wall, the tooth set 4 is not easy to get stuck in the first conical inner wall; similarly, when the tooth set 4 approaches the second tooth groove 31 on the second conical inner wall, the tooth set 4 is not easy to get stuck in the second conical inner wall.

[0038] Specifically, Figure 1 , Figure 3 and Figure 4As shown, in the axial section of the first conical inner wall, the opening angle of the first conical inner wall is 15 degrees to 90 degrees, and the first conical inner wall is coaxially arranged with the blocking rod 1; in the axial section of the second conical inner wall, the opening angle of the second conical inner wall is 15 degrees to 90 degrees, and the second conical inner wall is coaxially arranged with the blocking rod 1. In this way, when the tooth group 4 approaches the first tooth groove 21 on the first conical inner wall, the tooth group 4 is not easily stuck in the first conical inner wall; in addition, when the tooth group 4 approaches the first tooth groove 21 on the first conical inner wall along the shift lever 1 at a predetermined speed, there is a larger angle between the first conical inner wall and the tooth group 4, which reduces the squeezing force of the first conical inner wall on the tooth group 4 toward the shift lever 1, thereby avoiding the tooth group 4 from being squeezed and damaged; similarly, when the tooth group 4 approaches the second tooth groove 31 on the second conical inner wall, the tooth group 4 is not easily stuck in the second conical inner wall; in addition, when the tooth group 4 approaches the second tooth groove 21 on the second conical inner wall along the shift lever 1 at a predetermined speed, there is a larger angle between the second conical inner wall and the tooth group 4, which reduces the squeezing force of the second conical inner wall on the tooth group 4 toward the shift lever 1, thereby avoiding the tooth group 4 from being squeezed and damaged.

[0039] Specifically, Figure 1 , Figure 3 and Figure 4 As shown, the first conical inner wall and the second conical inner wall have the same shape. In this way, no matter the tooth set 4 cooperates with the first tooth groove 21 on the first conical inner wall or the tooth set 4 cooperates with the second tooth groove 31 on the second conical inner wall, the cooperation state can be kept consistent.

[0040] Specifically, Figure 1 , Figure 3 and Figure 4 As shown, the first conical inner wall, the second conical inner wall and the shift lever 1 are coaxially arranged. In this way, the shift lever 1 can move along its axis to approach the first conical inner wall, and the gear set 4 on the shift lever 1 can evenly contact the first conical inner wall; the shift lever 1 can move along its axis to approach the second conical inner wall, and the gear set 4 on the shift lever 1 can evenly contact the second conical inner wall.

[0041] Specifically, Figure 1 , Figure 3 and Figure 4 As shown, the diameter of the opening of the first conical inner wall is the same as the diameter of the opening of the second conical inner wall. In this way, when the tooth set 4 enters and exits the opening of the first conical inner wall and the opening of the second conical inner wall, the tooth set 4 is not easy to hit either the first conical inner wall or the second conical inner wall.

[0042] Specifically, Figure 1 , Figure 3 and Figure 4As shown, there is a release position on the moving path of the gear set 4; when the gear set 4 is located at the release position in the storage space, the gear set 4 is separated from the first tooth groove 21, and the gear set 4 is separated from the second tooth groove 31. In this way, the gear set 4 moves to the release position and can be separated from the first tooth groove 21 and the second tooth groove 31 respectively, thereby releasing the transmission state between the shift lever 1 and the first gear 2 and the second gear 3.

[0043] Specifically, Figure 1 , Figure 3 and Figure 4 As shown, the position where the tooth group 4 meshes with the first tooth groove 21 is the first position, and the position where the tooth group 4 meshes with the second tooth groove 31 is the second position; the distance that the tooth group 4 moves from the release position to the first position is the first distance, and the distance that the tooth group 4 moves from the release position to the second position is the second distance; the ratio of the first distance to the second distance is: 0.5-2. In this way, the tooth group 4 can move different distances from the release position along the shift lever 1 to mesh with the first tooth groove 21 or the second tooth groove 31 respectively, which is convenient for distinguishing the meshing of the tooth group 4 with the first tooth groove 21 or the second tooth groove 31; and it is prevented that the tooth group 4 meshes back and forth between the first tooth groove 21 or the second tooth groove 31 when the tooth group 4 is shifted / vibrated with equal amplitude between the first tooth groove 21 or the second tooth groove 31.

[0044] Specifically, in one embodiment, the gear set 4 has a first bevel gear that is conical and used to cooperate with the first tooth groove 21 and a second bevel gear that is conical and used to cooperate with the second tooth groove 31; the first bevel gear is adapted to the first conical inner wall, and the second bevel gear is adapted to the second conical inner wall. In this way, when the first bevel gear is inserted in the first conical inner wall and cooperates with the first tooth groove 21, the first bevel gear is not easy to shake; when the second bevel gear is inserted in the second conical inner wall and cooperates with the second tooth groove 31, the second bevel gear is not easy to shake.

[0045] Specifically, in one embodiment, the width of the first tooth groove 21 gradually increases in the axial direction from the vertex of the first conical inner wall to the opening. In this way, when the first conical gear is inserted into the first conical inner wall from the opening of the first conical inner wall, the teeth on the first conical gear are easily inserted into the first tooth groove 21.

[0046] Specifically, in one embodiment, the width of the second tooth groove 31 gradually increases in the axial direction from the vertex of the second conical inner wall to the opening. In this way, when the second conical gear is inserted into the second conical inner wall from the opening of the second conical inner wall, the teeth on the second conical gear are easily inserted into the second tooth groove 31.

[0047] Specifically, Figure 1 , Figure 3 and Figure 4As shown, the tooth set 4 includes a first helical tooth 41 and a second helical tooth 42 which are axially arranged and inclined in opposite directions. The first tooth groove 21 is used to cooperate with the first helical tooth 41, and the second tooth groove 31 is used to cooperate with the second helical tooth 42. It can be understood that Figure 6 and Figure 7 As shown, the shape of the first tooth groove 21 corresponds to the inclination direction of the first helical tooth 41, and the shape of the second tooth groove 31 corresponds to the inclination direction of the second helical tooth 42. In this way, the speed change mechanism uses the meshing and loosening states of the two sets of helical teeth and the tooth grooves in the gear to achieve multiple gears to control the shuttle to move forward. The arrangement of the first helical tooth 41 and the second helical tooth 42 facilitates the two ends of the tooth group 4 to be respectively inserted into the first tooth groove 21 and the second tooth groove 31, thereby improving the smoothness of the gear shift.

[0048] On the basis of the above structure, the shuttle speed change mechanism further includes a thrust bearing 5 sleeved on the shift lever 1, and the thrust bearing 5 is arranged between the first gear 2 and the second gear 3. By arranging the thrust bearing 5 between the first gear 2 and the second gear 3, the first gear 2 and the second gear 3 are blocked, so that the rotation connection between the first gear 2 and the second gear 3 can be ensured to be disconnected, and it is also helpful to avoid that when the shift lever 1 is pushed forward, the meshing friction between the second bevel teeth 42 and the second tooth groove 31 drives the second gear 3 to move toward the first gear 2, or when the shift lever 1 is moved backward, the meshing friction between the first bevel teeth 41 and the first tooth groove 21 drives the first gear 2 to move toward the second gear 3, thereby affecting the shifting performance.

[0049] Preferably, in this embodiment, an extension sleeve is provided at one end of the first gear 2 and the second gear 3 close to the thrust bearing 5, the extension sleeve on the first gear 2 is the first extension sleeve 22, and the extension sleeve on the second gear 3 is the second extension sleeve 32, and the thrust bearing 5 is sleeved on the two extension sleeves to facilitate the installation of the thrust bearing 5.

[0050] As a preferred embodiment, the highest ends of the first beveled teeth 41 and the second beveled teeth 42 are horizontally aligned and engaged, so as to avoid the smoothness of the gear shifting being affected by the gap between them. Preferably, the tooth length of the first tooth groove 21 is not greater than the length of the first beveled teeth 41, and the tooth length of the second tooth groove 31 is not greater than that of the second beveled teeth 42, which is conducive to the first beveled teeth 41 or the second beveled teeth 42 entering the corresponding tooth groove faster and more accurately, thereby improving the gear shifting efficiency.

[0051] Embodiment 2:

[0052] See also Figure 5As shown, the difference between the shift lever 1 in this embodiment and the embodiment 1 is that the tooth surfaces of the first bevel teeth 41 and the second bevel teeth 42 are arc-shaped, which is conducive to the first bevel teeth 41 and the second bevel teeth 42 entering the corresponding tooth grooves more smoothly, avoiding the jamming phenomenon of gear shifting, and even the phenomenon that the tip of the bevel teeth and the tooth groove are stuck during gear shifting, thereby affecting the life of the bevel teeth and the tooth groove. In this way, setting the tooth surface of the bevel teeth to be arc-shaped can further improve the smoothness of gear shifting.

[0053] Preferably, in this embodiment, see Figure 4 As shown, the inclination angle α of the first bevel tooth 41 is in the range of 3-30°, and the inclination angle α of the second bevel tooth 42 is in the range of 3-30°. Within this range, the service life of the bevel teeth and the tooth grooves can be improved. Preferably, the inclination angle α of the first bevel tooth 41 and the second bevel tooth 42 is 3-8°.

[0054] Further preferably, in order to increase the service life of the gear set 4 on the shift lever 1 , the shift lever 1 , the first bevel gear 41 and the second bevel gear 42 are an integrally formed structure, such as an integrally cast structure, so as to facilitate processing.

[0055] In summary, the shuttle speed change mechanism of the present invention switches the transmission connection between the first gear and the second gear through a shift lever with a gear set, thereby realizing speed change control of the shuttle, which is conducive to adapting to different terrain changes, thereby improving the operating safety performance of the shuttle, and the speed change mechanism has a simple and practical structure and low cost, and therefore has a high application and promotion value.

[0056] The above are only preferred embodiments of the present invention. It should be pointed out that, for ordinary technicians in this technical field, several improvements and substitutions can be made without departing from the technical principles of the present invention. These improvements and substitutions should also be regarded as the scope of protection of the present invention.

Claims

1. A shuttle speed change mechanism, characterized in that: The invention comprises a shift lever, and a first gear and a second gear sleeved on the shift lever and having different numbers of teeth; a gear set located between the first gear and the second gear is axially arranged on the outer circumference of the shift lever, a first tooth groove is arranged inside the first gear to be plugged with the first end of the tooth set, and a second tooth groove is arranged inside the second gear to be plugged with the second end of the tooth set; The shift lever moves axially back and forth so that the first end of the tooth set is inserted into the first tooth groove or the second end of the tooth set is inserted into the second tooth groove; The first gear has a first conical inner wall opening toward the second gear, and the second gear has a second conical inner wall opening toward the first gear; the first tooth groove is arranged on the first conical inner wall, and the second tooth groove is arranged on the second conical inner wall; a receiving space is formed between the first conical inner wall and the second conical inner wall, and the tooth set is located in the receiving space; The tooth set comprises a first helical tooth and a second helical tooth which are axially arranged and inclined in opposite directions, the first tooth groove is used to cooperate and plug with the first helical tooth, and the second tooth groove is used to cooperate and plug with the second helical tooth; the highest ends of the first helical tooth and the second helical tooth are horizontally aligned and engaged, so as to avoid the smoothness of the gear shifting being affected by the gap between the two; one end of the gear shift rod is used to be connected to the driving motor power, and the other end is used to be connected to the push-pull motor power, and the push-pull motor is connected to the end of the gear shift rod through a connecting sleeve; The shuttle speed change mechanism further includes a thrust bearing sleeved on the shift lever and arranged between the first gear and the second gear; an extension sleeve is provided on one end of the first gear and the second gear close to the thrust bearing, and the thrust bearing is sleeved on the extension sleeve; The angle between two generatrixes of the axial section of the first tapered inner wall is in the range of 15-90 degrees, and the angle between two generatrixes of the axial section of the second tapered inner wall is in the range of 15-90 degrees.

2. The shuttle speed change mechanism according to claim 1, characterized in that: The first tapered inner wall, the second tapered inner wall and the shift lever are coaxially arranged.

3. The shuttle speed change mechanism according to claim 1, characterized in that: The diameter of the opening of the first tapered inner wall is the same as the diameter of the opening of the second tapered inner wall.

4. The shuttle speed change mechanism according to claim 1, characterized in that: The moving path of the tooth group has a release position; when the tooth group is located at the release position in the storage space, the tooth group is separated from the first tooth groove, and the tooth group is separated from the second tooth groove.

5. The shuttle speed change mechanism according to claim 4, characterized in that: The position where the tooth group is meshed with the first tooth groove is the first position, and the position where the tooth group is meshed with the second tooth groove is the second position; the distance that the tooth group moves from the release position to the first position is the first distance, and the distance that the tooth group moves from the release position to the second position is the second distance; the ratio of the first distance to the second distance is: 0.5~2.

6. The shuttle speed change mechanism according to claim 1, characterized in that: The inclination angle α of the first oblique teeth is in the range of 3-30°, and the inclination angle α of the second oblique teeth is in the range of 3-30°.

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