阅读说明：本技术 一种穿梭机变速机构 (Speed change mechanism of shuttle machine ) 是由 马亚胜 张旭耀 黎树中 于 2020-12-04 设计创作，主要内容包括：本发明涉及索道运输设备领域,具体公开了一种穿梭机变速机构,其换挡杆、以及套设于换挡杆上且齿数不同的第一齿轮和第二齿轮；所述换挡杆的外周轴向设有位于所述第一齿轮和第二齿轮之间的齿组,第一齿轮的内部设有与齿组的第一端配合插接的第一齿槽,第二齿轮的内部设有与齿组的第二端配合插接的第二齿槽；换挡杆轴向来回移动以使所述齿组的第一端插接于第一齿槽或者使齿组的第二端插接于第二齿槽。本发明的穿梭机变速机构,其结构简单实用,具有多挡位结构,能实现对穿梭机的变速控制,有利于适应不同地形变化,提升穿梭机运行安全。(The invention relates to the field of cableway transportation equipment, and particularly discloses a speed change mechanism of a shuttle machine, which comprises a gear shift lever, a first gear and a second gear, wherein the first gear and the second gear are sleeved on the gear shift lever and have different tooth numbers; a gear group positioned between the first gear and the second gear is axially arranged on the periphery of the gear shift lever, a first tooth groove in matched and inserted connection with a first end of the gear group is formed in the first gear, and a second tooth groove in matched and inserted connection with a second end of the gear group is formed in the second gear; the gear shifting rod axially moves back and forth to enable the first end of the tooth group to be inserted into the first tooth groove or enable the second end of the tooth group to be inserted into the second tooth groove. The speed change mechanism of the shuttle machine is simple and practical in structure, has a multi-gear structure, can realize speed change control on the shuttle machine, is beneficial to adapting to different terrain changes, and improves the running safety of the shuttle machine.)

1. A speed change mechanism of a shuttle machine is characterized by comprising a gear shift lever, a first gear and a second gear, wherein the first gear and the second gear are sleeved on the gear shift lever and have different tooth numbers; a gear group positioned between the first gear and the second gear is axially arranged on the periphery of the gear shift lever, a first tooth groove in matched and inserted connection with a first end of the gear group is formed in the first gear, and a second tooth groove in matched and inserted connection with a second end of the gear group is formed in the second gear;

the gear shifting rod axially moves back and forth to enable the first end of the tooth group to be inserted into the first tooth groove or enable the second end of the tooth group to be inserted into the second tooth groove;

the first gear has a first tapered inner wall opening toward the second gear, and the second gear has a second tapered 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 group is located in the receiving space.

2. The shuttle machine shifting mechanism according to claim 1, wherein an angle between two generatrices of the axial cross-section of the first tapered inner wall ranges from 15 to 90 degrees, and an angle between two generatrices of the axial cross-section of the second tapered inner wall ranges from 15 to 90 degrees.

3. The shuttle machine shifting mechanism of claim 2, wherein the first tapered interior wall, the second tapered interior wall, and the shift lever are coaxially disposed.

4. The shuttle machine shifting mechanism of claim 2, wherein 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.

5. The shuttle machine shifting mechanism of claim 1, wherein the set of teeth have a release position in a path of movement; when the tooth group is located at a release position in the housing space, the tooth group is separated from the first tooth groove, and the tooth group is separated from the second tooth groove.

6. The shuttle transmission mechanism of claim 5, wherein the position at which the set of teeth mesh with the first tooth slot is a first position and the position at which the set of teeth mesh with the second tooth slot is a second position; the distance that the set of teeth moves from the release position to the first position is a first distance, and the distance that the set of teeth moves from the release position to the second position is a second distance; the first distance is equal to the second distance; the proportion value of the first distance to the second distance is as follows: 0.5 to 2.

7. The shuttle machine speed change mechanism according to claim 1, wherein the set of teeth includes first and second skewed teeth axially disposed and having opposite skew directions, the first tooth slot for mating engagement with the first skewed tooth, and the second tooth slot for mating engagement with the second skewed tooth.

8. The shuttle shifting mechanism of claim 7, further comprising a thrust bearing sleeved on the shift lever and disposed between the first gear and the second gear.

9. The shuttle machine speed change mechanism of claim 8, wherein an extension sleeve is disposed on each end of the first gear and the second gear proximate to the thrust bearing, and the thrust bearing is sleeved on the extension sleeve.

10. The shuttle transmission mechanism according to claim 7, wherein the first helical teeth have an angle of inclination a in the range of 3-30 ° and the second helical teeth have an angle of inclination a in the range of 3-30 °.

Technical Field

The invention relates to the technical field of cableway transportation equipment, in particular to a speed change mechanism of a shuttle machine.

Background

The use of cableways to transport goods is a traditional way of logistics transportation and is still used today in some situations. Transporting cargo on a cableway using a shuttle machine is an improvement over conventional cableway systems that facilitates faster and more efficient transportation of cargo to different destinations. The current shuttle machine is generally composed of a control component, a driving mechanism, and a boom mechanism connected with the control component and the driving mechanism, wherein the control component can control the driving mechanism to enable the driving mechanism to drive the shuttle machine to run along the cableway.

Different from the traditional technology, the ropeway is not only a single linear ropeway, but also the ropeway needs to turn under different terrains, but is limited by the limitation of a driving mechanism of the shuttle machine, the current commonly used shuttle machine can only run on the ropeway at a constant speed, the speed change cannot be realized during the turning, and due to the influence of centrifugal force, if the speed of the shuttle machine during the turning is not changed, the derailment is easy to occur, unnecessary danger can be caused, and the integral operation cost and the working efficiency of the ropeway system are greatly influenced. Therefore, in order to improve the operation safety factor of the shuttle machine, it is urgently needed to design a shuttle machine capable of changing speed, the speed is reduced to reduce the operation risk when the shuttle machine turns or goes downhill, the speed is properly increased when the shuttle machine goes uphill, thereby the climbing capability of the shuttle machine is avoided, and the phenomenon of stagnation or backward movement caused by heavy load is avoided so as to adapt to the operation requirements of different terrains.

In summary, the shuttle machine must be a transmission mechanism with a gear shifting and speed changing function to better utilize different speeds to achieve the purpose of adapting to different terrains, but most of the existing gear shifting and speed changing mechanisms are used for automobiles or motorcycles and electric vehicles, and the size and the weight of the existing gear shifting and speed changing mechanisms exceed the design requirements of the shuttle machine.

Disclosure of Invention

In order to solve the problems in the background art, the invention aims to provide a speed change mechanism of a shuttle machine, which has a simple and practical structure, has a multi-gear structure, can realize speed change control of the shuttle machine, is favorable for adapting to different terrain changes, and improves the running safety of the shuttle machine.

Based on this, the invention provides a shuttle machine speed change mechanism, which

The gear shifting device comprises a gear shifting rod, a first gear and a second gear, wherein the first gear and the second gear are sleeved on the gear shifting rod and have different tooth numbers; a gear group positioned between the first gear and the second gear is axially arranged on the periphery of the gear shift lever, a first tooth groove in matched and inserted connection with a first end of the gear group is formed in the first gear, and a second tooth groove in matched and inserted connection with a second end of the gear group is formed in the second gear;

the gear shifting rod axially moves back and forth to enable the first end of the tooth group to be inserted into the first tooth groove or enable the second end of the tooth group to be inserted into the second tooth groove;

the first gear has a first tapered inner wall opening toward the second gear, and the second gear has a second tapered 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 group is located in the receiving space.

Further, the included angle range between the two generatrices of the axial section of the first conical inner wall is 15-90 degrees, and the included angle range between the two generatrices of the axial section of the second conical inner wall is 15-90 degrees.

Further, the first tapered inner wall, the second tapered inner wall, and the shift lever are coaxially arranged.

Further, 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.

Further, the tooth group has a release position on a moving path thereof; when the tooth group is located at a release position in the housing space, the tooth group is separated from the first tooth groove, and the tooth group is separated from the second tooth groove.

Further, the position where the tooth group is meshed with the first tooth groove is a first position, and the position where the tooth group is meshed with the second tooth groove is a second position; the distance that the set of teeth moves from the release position to the first position is a first distance, and the distance that the set of teeth moves from the release position to the second position is a second distance; the first distance is equal to the second distance; the proportion value of the first distance to the second distance is as follows: 0.5 to 2.

Furthermore, the tooth group comprises a first helical tooth and a second helical tooth which are axially arranged and have opposite inclination directions, the first tooth groove is used for being matched and spliced with the first helical tooth, and the second tooth groove is used for being matched and spliced with the second helical tooth.

Further, the shuttle machine speed change mechanism further comprises a thrust bearing which is sleeved on the gear shift lever and is arranged between the first gear and the second gear.

Furthermore, one end of the first gear and one end of the second gear, which are tightly attached to the thrust bearing, are both provided with extension shaft sleeves, and the thrust bearing sleeves are arranged on the extension shaft sleeves.

Further, the inclination angle alpha of the first helical teeth ranges from 3 degrees to 30 degrees, and the inclination angle alpha of the second helical teeth ranges from 3 degrees to 30 degrees.

Compared with the prior art, the invention has the beneficial effects that:

the invention discloses a speed change mechanism of a shuttle machine, which comprises a gear shift lever, a first gear and a second gear, wherein the first gear and the second gear are sleeved on the gear shift lever, a first tooth groove is formed in the first gear, a second tooth groove is formed in the second gear, a tooth group is axially arranged on the periphery of the gear shift lever and is axially moved between the first gear and the second gear, the first end of the tooth group is inserted into the first tooth groove after the gear shift lever is pushed forwards, or the second end of the tooth group is inserted into the second tooth groove after the gear shift lever is retreated, so that when the first end of the tooth group is inserted into the first tooth groove to realize meshing, the second end of the tooth group is separated from the second tooth groove, and the first gear is driven by a corresponding external transmission component; when the second end of the gear group is inserted into the second gear groove to realize meshing, the first end of the gear group is separated from the first gear groove to realize the transmission of the second gear and a corresponding external transmission component, and the transmission is carried out by switching the first gear and the second gear due to the different tooth numbers of the first gear and the second gear, namely, the purpose of controlling the forward movement of the shuttle machine by using the meshing and releasing states of two ends of the gear group of the gear shift lever and the tooth grooves in the two gears is realized, so that the variable speed control of the shuttle machine can be realized, the variable speed control of the shuttle machine can be realized by having a plurality of gears, the variable speed control of the shuttle machine is favorable for adapting to different terrain changes, the operation safety performance of the shuttle machine is improved, meanwhile, the occupied volume of the traditional gear shift box is greatly reduced, the occupied volume and the weight are both reduced to the minimum, and the transmission shaft and the gear shift lever are designed in a combined, the speed change function of small volume and multiple gears is realized, and the overall design requirement of the shuttle machine is met.

Drawings

Fig. 1 is a schematic view of a shuttle machine shifting mechanism provided in accordance with an embodiment of the present invention;

fig. 2 is a perspective view of a shuttle shifting mechanism provided in accordance with an embodiment of the present invention;

fig. 3 is a schematic view of a tooth-shaped developed surface of a tooth set on a shift lever according to an embodiment of the present invention;

fig. 4 is a schematic view of a shift lever provided in the second embodiment of the present invention;

fig. 5 is a schematic view of a tooth-shaped developed surface of a tooth group on a shift lever according to a second embodiment of the present invention;

FIG. 6 is a schematic view of a first gear provided in accordance with a second embodiment of the present invention;

FIG. 7 is a schematic view of a second gear provided in accordance with a second embodiment of the present invention;

fig. 8 is a view showing a state in which the shift lever of the second embodiment of the present invention is pushed forward;

fig. 9 is a diagram showing a state of use when the shift lever according to the second embodiment of the present invention is retracted.

Wherein, 1, a gear shift lever; 2. a first gear; 21. a first tooth slot; 22. a first extension sleeve; 3. a second gear; 31. a second tooth slot; 32. a second extension sleeve; 4. a set of teeth; 41. a first helical tooth; 42. a second helical tooth; 5. a thrust bearing; 6. a drive motor; 7. a push-pull motor; 71. and the connecting shaft sleeve.

Detailed Description

The following detailed description of embodiments of the present invention is provided in connection with the accompanying drawings and examples. The following examples are intended to illustrate the invention but are not intended to limit the scope of the invention.

In the description of the present invention, it should be noted that the terms "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of description and simplicity of description, but do not indicate or imply that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the present invention. It should be understood that the terms "first", "second", etc. are used herein to describe various information, but the information should not be limited to these terms, which are only used to distinguish one type of information from another. For example, "first" information may also be referred to as "second" information, and similarly, "second" information may also be referred to as "first" information, without departing from the scope of the present invention.

The first embodiment is as follows:

referring to fig. 1 and 2, a shuttle transmission 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 disposed on the outer circumference of the shift lever 1, and the gear set 4 is located between the first gear 2 and the second gear 3, and importantly, a first tooth space 21 is disposed inside the first gear 2, a second tooth space 31 is disposed inside the second gear 3, the first tooth space 21 is adapted to be fittingly inserted into a first end of the gear set 4 (left end of the gear set 4 in fig. 1), and the second tooth space 31 is adapted to be fittingly inserted into a second end of the gear set 4 (right end of the gear set 4 in fig. 1).

In the shuttle transmission mechanism based on the above technical features, the gear set 4 is axially arranged on the outer periphery of the shift lever 1, and the gear set 4 is axially moved between the first gear 2 and the second gear 3, and the first end of the gear set 4 is inserted into the first tooth groove 21 by pushing the shift lever 1 forward (the shift lever 1 is moved leftward as shown in fig. 8), or the second end of the gear set 4 is inserted into the second tooth groove 31 by retreating (the shift lever 1 is moved rightward as shown in fig. 9) the shift lever 1, so that when the first end of the gear set 4 is inserted into the first tooth groove 21 to be engaged, the second end of the gear set 4 is separated from the second tooth groove 31, the first gear 2 starts to rotate, and the first gear 2 is driven by a corresponding external transmission component (such as a sun gear train); when the second end of the tooth group 4 is inserted into the second tooth groove 31 to realize meshing, the first end of the tooth group 4 is separated from the first tooth groove 21, the second gear 3 starts to rotate, the second gear 3 is driven by the corresponding external transmission component, since the numbers of teeth of the first gear 2 and the second gear 3 are different, the transmission is performed by switching the first gear 2 and the second gear 3, thereby enabling the speed change control of the shuttle machine, the speed change mechanism has simple and practical structure and a plurality of gears, can realize the speed change control of the shuttle machine, is beneficial to adapting to different terrain changes, thereby the operation security performance of shuttle has been promoted, and this speed change mechanism of shifting simultaneously significantly reduced the volume that occupies of traditional case of shifting, will occupy volume and weight and all reduce to minimum, with transmission shaft and gear level integrated design, realized the variable speed function of little volume many gears, accorded with the overall design requirement of shuttle. In the present embodiment, as shown in fig. 1, a first end of the shift lever 1 is used for being dynamically connected with the driving motor 6, a second end of the shift lever is used for being dynamically connected with the push-pull motor 7, the push-pull motor 7 is connected with a second section of the shift lever 1 through a connecting shaft 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 set 4 on the shift lever 1 is engaged with the first tooth groove 21 or the second end of the tooth set 4 is engaged with the second tooth groove 31, and the driving motor 6 drives the shift lever 1 to rotate, so as to realize rotation of the first gear 2 or rotation of the second gear 3, realize switching of gears, and further realize speed change control of the shuttle. Of course, in other embodiments, the second end of the shift lever 1 may be connected to the cylinder, as long as the push-pull function of the present invention can be achieved, and the details are not described herein.

Wherein the first gear 2 has a first tapered inner wall opening toward the second gear 3, and the second gear 3 has a second tapered inner wall 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 containing space is formed between the first conical inner wall and the second conical inner wall, and the tooth group 4 is positioned in the containing space. Therefore, the tooth group 4 is arranged in the accommodating space for protection, when the tooth group 4 approaches to the first tooth groove 21 on the first conical inner wall, the tooth group 4 is wrapped by the first conical inner wall, and the tooth group 4 is prevented from being separated from the first tooth groove 21 in the transmission process of the first tooth groove 21; when the tooth group 4 approaches to the second tooth groove 31 on the second conical inner wall, the tooth group 4 is wrapped by the second conical inner wall, so that the tooth group 4 is prevented from being separated from the second tooth groove 31 in the transmission process of the second tooth groove 31.

Specifically, as shown in fig. 1, 3 and 4, the included angle between two generatrices of the axial section of the first tapered inner wall ranges from 15 to 90 degrees, and the included angle between two generatrices of the axial section of the second tapered inner wall ranges from 15 to 90 degrees. Therefore, when the tooth group 4 approaches to the first tooth groove 21 on the first conical inner wall, the tooth group 4 is not easy to be clamped in the first conical inner wall; similarly, when the tooth group 4 approaches the second tooth groove 31 on the second tapered inner wall, the tooth group 4 is not easily stuck in the second tapered inner wall.

Specifically, as shown in fig. 1, 3 and 4, in the axial section of the first tapered inner wall, the opening angle of the first tapered inner wall is 15 degrees to 90 degrees, and the first tapered inner wall is arranged coaxially with the stopper 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 arranged coaxially with the stop lever 1. Therefore, when the tooth group 4 approaches to the first tooth groove 21 on the first conical inner wall, the tooth group 4 is not easy to be clamped in the first conical inner wall; in addition, when the gear group 4 is close to the first tooth groove 21 on the first conical inner wall along the gear shift lever 1 at a preset speed, a larger included angle is formed between the first conical inner wall and the gear group 4, so that the extrusion force of the gear group 4 to the gear shift lever 1 direction by the first conical inner wall is reduced, and the gear group 4 is prevented from being damaged by extrusion; similarly, when the tooth group 4 approaches to the second tooth groove 31 on the second conical inner wall, the tooth group 4 is not easy to be clamped in the second conical inner wall; in addition, when the tooth group 4 is close to the second tooth groove 21 on the second conical inner wall along the gear shifting lever 1 at a preset speed, a larger included angle is formed between the second conical inner wall and the tooth group 4, so that the extrusion force of the second conical inner wall to the gear shifting lever 1 from the tooth group 4 is reduced, and the tooth group 4 is prevented from being damaged by extrusion.

Specifically, as shown in fig. 1, 3 and 4, the first tapered inner wall and the second tapered inner wall have the same shape. In this way, whether the tooth group 4 is engaged with the first tooth groove 21 on the first tapered inner wall or the tooth group 4 is engaged with the second tooth groove 31 on the second tapered inner wall, the engaged state can be kept uniform.

Specifically, as shown in fig. 1, 3 and 4, the first tapered inner wall, the second tapered inner wall and the shift lever 1 are coaxially arranged. In this way, the gear shift lever 1 can be close to the first conical inner wall by moving along the axis, and the tooth group 4 on the gear shift lever 1 can be uniformly contacted with the first conical inner wall; the shift lever 1 can be moved along its axis to approach the second tapered inner wall, and the set of teeth 4 on the shift lever 1 can be uniformly contacted with the second tapered inner wall.

Specifically, as shown in fig. 1, 3 and 4, 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. So, when tooth group 4 passed in and out the opening of first toper inner wall and the opening of second toper inner wall, tooth group 4 was difficult to collide with arbitrary one in first toper inner wall or the second toper inner wall.

Specifically, as shown in fig. 1, 3 and 4, the tooth group 4 has a release position on the moving path; when the teeth group 4 is located at the release position in the housing space, the teeth group 4 is separated from the first tooth groove 21, and the teeth group 4 is separated from the second tooth groove 31. Thus, the set of teeth 4 can be separated from the first and second tooth grooves 21 and 31, respectively, when moved to the release position, thereby releasing the gear shift lever 1 from the transmission state with the first and second gears 2 and 3.

Specifically, as shown in fig. 1, 3 and 4, the position where the tooth group 4 meshes with the first tooth groove 21 is a first position, and the position where the tooth group 4 meshes with the second tooth groove 31 is a second position; the distance that the set of teeth 4 moves from the release position to the first position is a first distance, and the distance that the set of teeth 4 moves from the release position to the second position is a second distance; the ratio of the first distance to the second distance is: 0.5 to 2. In this way, the set of teeth 4 can move along the shift lever 1 from the release position by different distances to engage with the first tooth groove 21 or the second tooth groove 31, respectively, so as to distinguish the engagement of the set of teeth 4 with the first tooth groove 21 or the second tooth groove 31; and the tooth group 4 is prevented from meshing with the first tooth groove 21 or the second tooth groove 31 back and forth when the tooth group 4 shifts/vibrates in the first tooth groove 21 or the second tooth groove 31 at the same amplitude.

Specifically, in one embodiment, the set of teeth 4 has a first bevel gear having a conical shape and adapted to cooperate with the first tooth slot 21 and a second bevel gear having a conical shape and adapted to cooperate with the second tooth slot 31; the first bevel gear is matched with the first conical inner wall, and the second bevel gear is matched with the second conical inner wall. Therefore, when the first conical gear is inserted into the first conical inner wall and matched with the first tooth groove 21, the first conical gear is not easy to shake; when the second bevel gear is inserted into the second bevel inner wall to match with the second gear groove 31, the second bevel gear is not easy to shake.

Specifically, in one embodiment, the width of the first tooth slot 21 is gradually increased in the axial direction of the first tapered inner wall toward the opening at the apex thereof. Thus, when the first bevel gear is clamped into the first tapered inner wall from the first tapered inner wall opening, the teeth on the first bevel gear are easily clamped into the first tooth groove 21.

Specifically, in one embodiment, the width of the second tooth groove 31 gradually increases in the axial direction of the second tapered inner wall from the apex toward the opening. In this way, when the second bevel gear is engaged into the second bevel inner wall from the second bevel inner wall opening, the teeth on the second bevel gear are easily engaged into the second grooves 31.

Specifically, as shown in fig. 1, 3 and 4, the tooth group 4 includes a first helical tooth 41 and a second helical tooth 42 which are axially arranged and have opposite inclination directions, the first tooth space 21 is used for being matched and inserted with the first helical tooth 41, and the second tooth space 31 is used for being matched and inserted with the second helical tooth 42, it can be understood that, as shown in fig. 6 and 7, the shape of the first tooth space 21 corresponds to the inclination direction of the first helical tooth 41, and the shape of the second tooth space 31 corresponds to the inclination direction of the second helical tooth 42, so that the speed change mechanism utilizes the engagement and disengagement states of the two sets of helical teeth and the tooth spaces in the gears to realize multiple gears so as to control the forward movement of the shuttle machine. Through the arrangement of the first helical teeth 41 and the second helical teeth 42, the two ends of the tooth group 4 can be conveniently and correspondingly inserted into the first tooth groove 21 and the second tooth groove 31 respectively, and the gear shifting smoothness is improved.

On the basis of the structure, the speed change mechanism of the shuttle machine further comprises a thrust bearing 5 sleeved on the gear shift lever 1, and the thrust bearing 5 is arranged between the first gear 2 and the second gear 3. Through set up thrust bearing 5 between first gear 2 and second gear 3, separation first gear 2 and second gear 3, so can ensure to break off the rotation between first gear 2 and the second gear 3 and be connected, be favorable to avoiding simultaneously when pushing away in the front gear shift lever 1 because the second skewed tooth 42 drives second gear 3 and follows towards first gear 2 with the meshing friction of second tooth's socket 31 and remove, perhaps because the meshing friction of first skewed tooth 41 and first tooth's socket 21 drives first gear 2 and follows towards second gear 3 and remove when backing gear shift lever 1, thereby influence the performance of shifting.

Preferably, in this embodiment, the first gear 2 and the second gear 3 are provided with an extension shaft sleeve at one end close to the thrust bearing 5, the extension shaft sleeve on the first gear 2 is a first extension shaft sleeve 22, the extension shaft sleeve on the second gear 3 is a second extension shaft sleeve 32, and the thrust bearing 5 is sleeved on the two extension shaft sleeves, so as to facilitate the installation of the thrust bearing 5.

In a preferred embodiment, the highest ends of the first helical teeth 41 and the second helical teeth 42 are horizontally aligned and engaged, so that the influence on the smoothness of the gear shifting caused by the occurrence of a gap between the two is avoided. Preferably, the length of the first tooth slot 21 is not greater than that of the first helical tooth 41, and the length of the second tooth slot 31 is not greater than that of the second helical tooth 42, so that the first helical tooth 41 or the second helical tooth 42 can enter the corresponding tooth slot more quickly and accurately, and the gear shifting efficiency is improved.

Example two:

referring to fig. 5, the difference between the shift lever 1 of the present embodiment and the first embodiment is that the tooth surfaces of the first helical tooth 41 and the second helical tooth 42 are arc-shaped, which is beneficial for the first helical tooth 41 and the second helical tooth 42 to enter the corresponding tooth grooves more smoothly, so as to avoid the cogging phenomenon of shifting, even the tip of the helical tooth and the tooth groove are pushed up during shifting, thereby affecting the life of the helical tooth and the tooth groove, so that the tooth surfaces of the helical tooth are arc-shaped, and the smoothness of shifting can be further improved.

Preferably, in the present embodiment, as shown in fig. 4, the inclination angle α of the first helical teeth 41 is in the range of 3 to 30 °, and the inclination angle α of the second helical teeth 42 is in the range of 3 to 30 °, within which the life span of the helical teeth and the tooth grooves can be improved, and preferably, the inclination angle α of the first helical teeth 41 and the second helical teeth 42 is in the range of 3 to 8 °.

Further preferably, in order to improve the service life of the set of teeth 4 on the shift lever 1, the first helical tooth 41 and the second helical tooth 42 are of an integrally molded structure, for example, an integrally cast structure, so as to facilitate the machining.

In summary, the shuttle machine speed change mechanism of the invention switches the transmission connection of the first gear and the second gear through the gear shift lever with the gear set, thereby realizing the speed change control of the shuttle machine, being beneficial to adapting to different terrain changes, and improving the operation safety performance of the shuttle machine.

The above is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, several modifications and substitutions can be made without departing from the technical principle of the present invention, and these modifications and substitutions should also be regarded as the protection scope of the present invention.