transmission

Abstract

The present invention discloses a transmission, which relates to the technical field of speed change equipment. The transmission comprises a semi-gear ring with a non-fixed position, a transmission plate driven to rotate by a driver, a first speed change rail fixedly connected to the transmission plate, a first power gear capable of moving and axially rotating along the first speed change rail, a first transmission shaft driven to rotate by the first power gear, and a first output gear driven to rotate by the first transmission shaft. The transmission plate, the first speed change rail, the first power gear, and the first transmission shaft are all located on the front side of the semi-gear ring; the transmission also comprises a second speed change rail fixedly connected to the transmission plate, a second power gear capable of moving and axially rotating along the second speed change rail, a second transmission shaft driven to rotate by the second power gear, and a second output gear driven to rotate by the second transmission shaft. The transmission plate, the second speed change rail, the second power gear, and the second transmission shaft are all located on the back side of the semi-gear ring.

Description

Technical Field

[0001] The present invention relates to the technical field of speed change equipment, and in particular to a speed changer. Background Art

[0002] The transmission, located between the engine and the driving mechanism, is used to change the input-output transmission ratio, achieving speed changes. Existing transmissions include continuously variable transmissions (CVTs), which consist of a pulley and a metal belt, with the pulley consisting of two wheels. CVTs achieve different speed conversions by narrowing or widening the spacing between the wheels to change the diameter of the metal belt in contact with the pulley. This speed-changing method results in a relatively low maximum torque and slightly poor stability. Therefore, when subjected to high torque power, CVTs place stringent requirements on the drive chain, requiring it to prevent breakage or slippage. CVTs are also more likely to experience problems during use. Due to the limited force that their drive chains can withstand, most models equipped with CVTs experience a lack of stamina.

[0003] In order to eliminate the disadvantages brought by the transmission chain, another type of transmission has appeared on the market, which is the transmission used in most existing vehicles. This type of transmission achieves speed change by meshing gears of different diameters. Due to the limited number of gears, the speed gears of this type of transmission are limited, and when shifting gears, the gear meshing object is changed, which will be accompanied by a sense of jerk. Summary of the Invention

[0004] The object of the present invention is to provide a transmission that does not require a transmission chain and does not change the meshing gears in order to solve the above-mentioned problems.

[0005] The technical solution adopted in the present invention is as follows:

[0006] A transmission comprises a half-toothed ring with a fixed position, a transmission plate driven to rotate by a driver, a first speed-changing rail fixedly connected to the transmission plate, a first power gear capable of moving and axially rotating along the first speed-changing rail, a first transmission shaft driven to rotate by the first power gear, and a first output gear driven to rotate by the first transmission shaft, the transmission plate, the first speed-changing rail, the first power gear, and the first transmission shaft are all located on the front side of the half-toothed ring; and further comprises a second speed-changing rail fixedly connected to the transmission plate, a second power gear capable of moving and axially rotating along the second speed-changing rail, a second transmission shaft driven to rotate by the second power gear, and a second output gear driven to rotate by the second transmission shaft, the transmission plate, the second speed-changing rail, the second power gear, and the second transmission shaft. The transmission shafts are all located on the back of the half-toothed ring; the first speed change rail and the second speed change rail are arranged in parallel and staggered, and the two have the same rotation path but never overlap; a differential gear is engaged between the first output gear and the second output gear to neutralize the speed difference between the two output gears; when changing speed, the half-toothed ring is moved to change the distance between the half-toothed ring and the transmission plate, and the half-toothed ring pushes the first power gear to move along the first speed change rail and pushes the second power gear to move along the second speed change rail. By changing the distance between the first power gear and the second power gear relative to the transmission plate, the speed of the first power gear and the second power gear engaging with the half-toothed ring is changed, thereby changing the rotation speed of the first output gear and the second output gear, and then changing the speed neutralized to the differential gear.

[0007] Using this technical solution, the drive connected to the drive plate is shifted through the meshing of the gears, and then output through the differential gear. Speed ​​changes are achieved by adjusting the position of the half-ring gear. Since the half-ring gear position is unrestricted, the speed range is also unrestricted. Speed ​​changes can be achieved by slowly and evenly moving the half-ring gear, ensuring smooth, jerk-free shifting.

[0008] Preferably, the front and back sides of the half-toothed ring are respectively provided with meshing teeth for engaging the first power gear and the second power gear; the front and back sides of the half-toothed ring are both provided with positioning tracks along the circumferential direction; the first power gear is axially extended with a first slider, which can be embedded in the positioning track on the front side of the half-toothed ring and move along the positioning track; the second power gear is axially extended with a second slider, which can be embedded in the positioning track on the back side of the half-toothed ring and move along the positioning track.

[0009] By adopting the above technical solution, the first power gear and the second power gear can move along the positioning track, limiting the moving trajectory of the first power gear and the second power gear on the half-toothed ring; when the half-toothed ring changes its position, the positioning track is used to prevent the first power gear and the second power gear from completely disengaging from the half-toothed ring and being unable to engage with the half-toothed ring.

[0010] Preferably, at least two first speed change rails are provided on the front side of the half gear ring, and the first power gears on the two first speed change rails are alternately meshed with the half gear ring.

[0011] Preferably, at least two second speed change rails are provided on the back of the half gear ring, and the second power gears on the two second speed change rails are alternately meshed with the half gear ring.

[0012] By adopting the above technical solution, the smoothness of the speed change is guaranteed during the speed change process.

[0013] Preferably, a first limit block is fixed on the front side of the semi-toothed ring, the first limit block is coaxial and concentric with the semi-toothed ring, one end of the first transmission shaft abuts against the first limit block, and during the circumferential rotation of the first transmission shaft, one end thereof moves along the first limit block, and the first limit block is fan-shaped.

[0014] Preferably, a second limit block is fixed on the back of the semi-toothed ring, the second limit block is coaxial and concentric with the semi-toothed ring, one end of the second transmission shaft abuts against the second limit block, and during the circumferential rotation of the second transmission shaft, one end thereof moves along the second limit block, and the second limit block is fan-shaped.

[0015] By adopting the above technical solution, the first limit block and the second limit block enable the first transmission shaft and the second transmission shaft to reciprocate along the direction of the extended diameter of the transmission disk during the circumferential rotation.

[0016] Preferably, the differential gear is rotatably connected to an output shaft, the axis of the output shaft is perpendicular to the axis of the differential gear, the output shaft is driven to rotate by the differential gear, and the power of the driver is output through the output shaft.

[0017] By adopting the above technical solution, the first output gear and the second output gear are neutralized by the differential gear and finally output through the output shaft.

[0018] Preferably, the first power gear is always engaged with the first transmission gear, the first transmission gear is arranged on the first transmission shaft and can move along the first transmission shaft, the rotation of the first power gear drives the first transmission gear to rotate, and the first transmission gear drives the first transmission shaft to rotate axially; the second power gear is always engaged with the second transmission gear, the second transmission gear is arranged on the second transmission shaft and can move along the second transmission shaft, the rotation of the second power gear drives the second transmission gear to rotate, and the second transmission gear drives the second transmission shaft to rotate axially.

[0019] Using this technical solution, the first power gear drives the first transmission shaft by meshing with the first transmission gear; the second power gear drives the second transmission shaft by meshing with the second transmission gear. This same gear meshing ensures smooth and stable power transmission during operation. The first power gear and the first transmission shaft, and the second power gear and the second transmission shaft, rotate in different directions, allowing power to be smoothly transmitted in two different directions through the first and second transmission gears.

[0020] Preferably, a first belt gear is fixed at a position near the end of one end of the first transmission shaft, and the first belt gear is meshed with a third output gear. The third output gear is coaxial and concentric with the first output gear, and the third output gear drives the first output gear to rotate synchronously. The first transmission shaft rotates axially, driving the first belt gear to rotate, and the first belt gear drives the third output gear to rotate, and the third output gear drives the first output gear to rotate; a second belt gear is fixed at a position near the end of one end of the second transmission shaft, and the second belt gear is meshed with a fourth output gear. The fourth output gear is coaxial and concentric with the second output gear, and the fourth output gear drives the second output gear to rotate synchronously. The second transmission shaft rotates axially, driving the second belt gear to rotate, and the second belt gear drives the fourth output gear to rotate, and the fourth output gear drives the second output gear to rotate.

[0021] Using the above technical solution, the first transmission shaft drives the first output gear through the cooperation of the first belt gear and the third output gear; the second transmission shaft drives the second output gear through the cooperation of the second belt gear and the fourth output gear. Both gears engage, ensuring smooth and stable power transmission during operation. The first transmission shaft and the first output gear, and the second transmission shaft and the second output gear, rotate in different directions. Through the cooperation of the first belt gear and the third output gear, and the second belt gear and the fourth output gear, power in two different rotational directions is smoothly transmitted.

[0022] Preferably, the first power gear and the first transmission gear are meshed through a first intermediate transmission gear, the first intermediate transmission gear and the first power gear are coaxial and concentric, the two are fixedly connected and rotate synchronously, and the first intermediate transmission gear is meshed with the first transmission gear; the second power gear and the second transmission gear are meshed through a second intermediate transmission gear, the second intermediate transmission gear and the second power gear are coaxial and concentric, the two are fixedly connected and rotate synchronously, and the second intermediate transmission gear is meshed with the second transmission gear.

[0023] With the above technical solution, the first power gear drives the first transmission gear via the first intermediate gear, and the second power gear drives the second transmission gear via the second intermediate gear, both of which engage with each other, ensuring smooth and stable power transmission during operation. An intermediate gear meshing connection is added between the first power gear and the first transmission gear, and between the second power gear and the second transmission gear, respectively, to prevent interference between the first power gear's meshing with the half-toothed ring and its driving the first transmission gear, and to prevent interference between the second power gear's meshing with the half-toothed ring and its driving the second transmission gear.

[0024] In summary, due to the adoption of the above technical solution, the beneficial effects of the present invention are as follows: the power of the driver is directly transmitted to the transmission disc, and then transmitted from the transmission disc to the first speed change rail and the second speed change rail. The first speed change rail and the second speed change rail respectively drive the first power gear and the second power gear to engage with the half-toothed ring. The first power gear and the second power gear generate power for axial rotation by engaging with the half-toothed ring and moving relative to the half-toothed ring. The power is then transmitted to the first transmission shaft and the second transmission shaft respectively, and then transmitted from the first transmission shaft and the second transmission shaft to the first output gear and the second output gear. The first output gear and the second output gear are differentially neutralized and then output through the differential gear. The above is the power output process of the entire driver. The entire process is achieved entirely through gear meshing, without the provision of a transmission chain similar to a continuously variable transmission, thus avoiding the disadvantages brought by the transmission chain.

[0025] During speed changes, the distance between the half-gear ring and the transmission disc is moved. By changing the distance between the first and second power gears and the transmission disc, the speed at which the first and second power gears move relative to the half-gear ring when engaging with it is altered, thereby changing the rotational speeds of the first and second output gears. Because the distance between the half-gear ring and the transmission disc is not fixed, the speed range is unlimited, allowing for multiple speed changes based on actual needs. Furthermore, the gear meshing partner does not need to be changed during the speed change process, eliminating any sense of jerkiness. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] Figure 1 It is a structural schematic diagram of the present invention.

[0027] Figure 2 for Figure 1 A partial enlarged view of middle A.

[0028] Figure 3 for Figure 1 A partial enlarged view of B.

[0029] Figure 4 for Figure 1 Schematic diagram of the structure from another angle.

[0030] Figure 5 for Figure 4 A partial enlarged view of C in the middle.

[0031] Figure 6 for Figure 4 A partial enlarged view of D in the middle.

[0032] Figure 7 For the present invention Figure 1 Schematic diagram of the structure after changing the position of the half gear ring based on the position of the gear.

[0033] Figure 8 for Figure 7Schematic diagram of the structure from another angle.

[0034] Figure 9 It is a structural diagram of the coordination of the connecting plate, the first speed change rail, the first power gear, the first intermediate gear, the first transmission gear, the first transmission shaft, the first belt gear, and the first limit block.

[0035] Figure 10 It is a structural diagram of the coordination of the second power gear, the second intermediate gear, the second transmission gear, the second transmission shaft, and the second rotating gear.

[0036] Figure 11 It is a structural diagram of the coordination among the first power gear, the first intermediate gear and the first transmission gear.

[0037] Figure 12 This is a structural diagram of the coordination of the first transmission shaft, the second transmission shaft, the first belt rotating gear, the second belt rotating gear, the third output gear, the fourth output gear, the first output gear, the second output gear, the differential gear, and the first limit block.

[0038] Figure 13 This is a schematic diagram of the structure of the coordination among the third output gear, the fourth output gear, the first output gear, the second output gear, the differential gear, and the output shaft.

[0039] Figure 14 It is a partial enlarged view of the cooperation between the half gear ring, the first speed change rail, the first power gear, the first intermediate gear, the first transmission gear, and the first transmission shaft, wherein the first slider is embedded in the meshing track, and the first power gear is meshed with the half gear ring.

[0040] Figure 15 This is the front view of the half gear ring.

[0041] Markings in the figure: half gear ring-1, positioning rail-101, meshing rail-102, disengaging rail-103, transmission plate-2, connecting plate-3, first speed change rail-4, second speed change rail-5, first power gear-6, first slider-601, second power gear-7, second slider-701, first intermediate transmission gear-8, second intermediate transmission gear-9, first transmission gear-10, second transmission gear-11, first transmission shaft-12, second transmission shaft-13, first belt rotating gear-14, second belt rotating gear-15, third output gear-16, fourth output gear-17, first output gear-18, second output gear-19, differential gear-20, output shaft-21, first limit block-22, second limit block-23, transmission plate-24. DETAILED DESCRIPTION

[0042] The present invention will be described in detail below with reference to the accompanying drawings.

[0043] In order to make the purpose, technical solutions and advantages of the present invention more clearly understood, the present invention will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present invention and are not intended to limit the present invention.

[0044] Please see Figures 1 to 15 A transmission includes an annular half-gear ring 1, which is not fixed in position and never rotates. Meshing teeth are provided on the inner ring positions of the front and back surfaces, and relative and identical positioning tracks 101 are opened on the front and back surfaces along the circumferential direction. The middle part of the positioning track 101 is close to the meshing teeth, and this section of the positioning track 101 is recorded as the meshing track 102. The remaining edge part is away from the meshing teeth, and this section of the positioning track 101 is recorded as the disengagement track 103.

[0045] The drive disc 2 is annular and has meshing teeth on its outer ring. The meshing teeth are fixedly connected to a driver. The driving end of the driver drives the drive disc 2 to rotate axially via the meshing teeth connected to the drive disc 2. The driver is a combination of a motor and a reducer.

[0046] The transmission disc 2 has three connecting plates 3 extending toward the back of the half gear ring 1. The connecting plates 3 are evenly distributed along the circumference of the transmission disc 2. The connecting plates 3 are perpendicular to the transmission disc 2. The axial rotation of the transmission disc 2 drives the connecting plates 3 to rotate synchronously with the transmission disc 2 in the same direction.

[0047] The three connecting plates 3 are respectively fixedly connected with three first speed shift rails 4, the connecting plates 3 are fixedly connected with a transmission plate 24, and the transmission plate 24 is fixedly connected with three second speed shift rails 5. The first speed shift rail 4 is located on the front side of the half gear ring 1, and the second speed shift rail 5 is located on the back side of the half gear ring 1. The first speed shift rail 4 and the second speed shift rail 5 are staggered. The angle between each first speed shift rail 4 and its adjacent second speed shift rail 5 is 60°, and the angle between every two adjacent first speed shift rails 4 and every two adjacent second speed shift rails 5 are both 120°. Both the first speed shift rail 4 and the second speed shift rail 5 are perpendicular to the connecting plate 3 and parallel to the transmission disc 2. The axial rotation of the transmission disc 2 drives the first speed shift rail 4 and the second speed shift rail 5 to rotate synchronously with the transmission disc 2 in the same direction.

[0048] One end of the first speed-change rail 4 is fixed to the connecting plate 3, and the other end is rotatably and slidably connected to the first power gear 6. The first power gear 6 can rotate axially about the connection point with the first speed-change rail 4, and can also move along the first speed-change rail 4. A first slider 601 extends axially from the first power gear 6. The first slider 601 is embedded in the positioning track 101 on the front of the semi-gear ring 1 and moves along the positioning track 101. The rotation of the first speed-change rail 4 drives the first power gear 6 to move to the positioning track 101 along the front of the semi-gear ring 1. When the first power gear 6 moves to the meshing track 102 of the positioning track 101, the first power gear 6 meshes with the semi-gear ring 1. When the first power gear 6 moves to the disengagement track 103 of the positioning track 101, the first power gear 6 disengages from the semi-gear ring 1. One end of the second speed-change rail 5 is fixed to the transmission plate 24, and the other end is rotatably and slidably connected to the second power gear 7. The second power gear 7 can rotate axially about the connection point with the second speed-change rail 5 and can also move along the second speed-change rail 5. A second slider 701 extends axially from the second power gear 7. The second slider 701 can be embedded in the positioning track 101 on the back of the semi-gear ring 1 and move along the positioning track 101. The rotation of the second speed-change rail 5 drives the second power gear 7 to move to the positioning track 101 along the back of the semi-gear ring 1. When the second power gear 7 moves to the meshing track 102 of the positioning track 101, the second power gear 7 meshes with the semi-gear ring 1. When the second power gear 7 moves to the disengagement track 103 of the positioning track 101, the second power gear 7 disengages from the semi-gear ring 1.

[0049] The first power gear 6 is axially fixedly connected to the first intermediate gear 8, and the two are parallel. The first slider 601 and the first intermediate gear 8 are located on opposite sides of the first power gear 6, and the first speed change rail 4 is located between the first power gear 6 and the first intermediate gear 8. The first intermediate gear 8 is driven by the first power gear 6 and rotates synchronously with the first power gear 6 in the same direction. The second power gear 7 is axially fixedly connected to the second intermediate gear 9, and the two are parallel. The second slider 701 and the second intermediate gear 9 are located on opposite sides of the second power gear 7, and the second speed change rail 5 is located between the second power gear 7 and the second intermediate gear 9. The second intermediate gear 9 is driven by the second power gear 7 and rotates synchronously with the second power gear 7 in the same direction.

[0050] The first intermediate gear 8 is meshed with the first transmission gear 10, with their axes perpendicular. Axial rotation of the first intermediate gear 8 drives axial rotation of the first transmission gear 10. The second intermediate gear 9 is meshed with the second transmission gear 11, with their axes perpendicular. Axial rotation of the second intermediate gear 9 drives axial rotation of the second transmission gear 11. The first intermediate gear 8 prevents interference between the first power gear 6 engaging the half ring gear 1 and driving the first transmission gear 10. The second intermediate gear 9 prevents interference between the second power gear 7 engaging the half ring gear 1 and driving the second transmission gear 11.

[0051] The axis of the first transmission gear 10 is penetrated by the first transmission shaft 12, and the two are coaxial, concentric and slidingly connected. The first transmission gear 10 can move along the first transmission shaft 12; the first transmission shaft 12 is parallel to the first speed change rail 4, and the end of the first transmission shaft 12 away from the first transmission gear 10 is rotated and slidingly connected with the connecting plate 3, and the connecting plate 3 connects the first speed change rail 4 and the first transmission shaft 12 which are parallel to each other. The first transmission shaft 12 can rotate axially relative to the connecting plate 3 and rotate with the connecting plate 3; the first transmission gear 10 rotates axially, driving the first transmission shaft 12 to rotate axially; when the first power gear 6 moves along the first speed change rail 4, it drives the first intermediate transmission gear 8 to move synchronously in the same direction, and then drives the first transmission gear 10 to move along the first transmission shaft 12. The second transmission shaft 13 is passed through the axis of the second transmission gear 11, and the two are coaxial, concentric and slidingly connected. The second transmission gear 11 can move along the second transmission shaft 13; the second transmission shaft 13 is parallel to the second speed change rail 5, and the end of the second transmission shaft 13 away from the second transmission gear 11 is rotated and slidably connected with the connecting plate 3, and the connecting plate 3 connects the first speed change rail 4 and the first transmission shaft 12 which are parallel to each other. The second transmission shaft 13 can rotate axially relative to the connecting plate 3 and rotate together with the connecting plate 3; the second transmission gear 11 rotates axially, driving the second transmission shaft 13 to rotate axially; when the second power gear 7 moves along the second speed change rail 5, it drives the second intermediate transmission gear 9 to move synchronously in the same direction, thereby driving the second transmission gear 11 to move along the second transmission shaft 13.

[0052] The first transmission shaft 12 is fixedly connected to a first rotating gear 14 at one end near the connecting plate 3. The first rotating gear 14 is parallel to the first transmission gear 10 and is driven by the first transmission shaft 12 to rotate synchronously in the same direction. The second transmission shaft 13 is fixedly connected to a second rotating gear 15 at one end near the transmission plate 24. The second rotating gear 15 is parallel to the second transmission gear 11 and is driven by the second transmission shaft 13 to rotate synchronously in the same direction.

[0053] The first belt rotating gear 14 is meshedly connected to the third output gear 16, and the axes of the first belt rotating gear 14 and the third output gear 16 are perpendicular to each other. The axial rotation of the first belt rotating gear 14 drives the axial rotation of the third output gear 16. The second belt rotating gear 15 is meshedly connected to the fourth output gear 17, and the axes of the second belt rotating gear 15 and the fourth output gear 17 are perpendicular to each other.

[0054] The third output gear 16 is axially fixedly connected to the first output gear 18, and the two are parallel. The first output gear 18 is driven by the third output gear 16 to rotate synchronously in the same direction. The fourth output gear 17 is axially fixedly connected to the second output gear 19, and the two are parallel. The second output gear 19 is driven by the fourth output gear 17 to rotate synchronously in the same direction.

[0055] A differential gear 20 is meshed and connected between the first output gear 18 and the second output gear 19. The axis of the differential gear 20 is perpendicular to the first output gear 18 and the second output gear 19. The differential gear 20 is driven by the first output gear 18 and the second output gear 19 to rotate axially, neutralizing the speed of the first output gear 18 and the second output gear 19. There are two differential gears 20 arranged in parallel, and the two differential gears 20 are rotationally connected, and the midpoint of the axis connection line of the two differential gears 20 is located on the extended axis of the transmission plate 2.

[0056] The transmission plate 2, the third output gear 16, the first output gear 18, the second output gear 19, and the fourth output gear 17 are coaxial and concentric, and are arranged in sequence from the front to the back of the gears.

[0057] The axes of the first output gear 18, the second output gear 19, the third output gear 16, and the fourth output gear 17 penetrate and are rotatably connected to the output shaft 21. The output shaft 21 is rotatably connected to the differential gear 20. The first output gear 18 and the second output gear 19 are neutralized by the differential gear 20 and transmitted to the output shaft 21 by the differential gear 20 for output. The two differential gears 20 rotate axially and circumferentially. When the two differential gears 20 rotate circumferentially, the output shaft 21 is driven to rotate axially.

[0058] The output shaft 21 is rotatably connected to a first limit block 22, and the output shaft 21 can rotate relative to the first limit block 22, and the first limit block 22 is always stationary; one end of the first transmission shaft 12 close to the connecting plate 3 always abuts against the first limit block 22; the first limit block 22 is a two-thirds sector, and the central angle of the first limit block 22 is 240°. The meshing track 102 of the front positioning track 101 of the semi-toothed ring 1 is opposite to the sector-shaped recessed part of the first limit block 22, and the disengagement track 103 of the front positioning track 101 of the semi-toothed ring 1 is opposite to the sector-shaped protrusion of the first limit block 22; when the first transmission shaft 12 abuts against the sector-shaped recessed part of the first limit block 22, the first power gear 6 corresponding to the first transmission shaft 12 is located at the semi-toothed ring 1 In the meshing track 102 of the front positioning track 101, the first power gear 6 is meshed with the half-toothed ring 1, and the first rotating gear 14 corresponding to the first transmission shaft 12 is meshed with the third output gear 16; when the first transmission shaft 12 abuts against the fan-shaped protrusion of the first limit block 22, the first power gear 6 corresponding to the first transmission shaft 12 is located in the meshing track 102 or the disengagement track 103 of the front positioning track 101 of the half-toothed ring 1, the first power gear 6 is meshed with or disengaged from the half-toothed ring 1, and the first rotating gear 14 corresponding to the first transmission shaft 12 is disengaged from the third output gear 16; the first limit block 22 is used to ensure that at each moment, only one first rotating gear 14 is meshed with the third output gear 16. The output shaft 21 is rotatably connected to a second limit block 23, and the output shaft 21 can rotate relative to the second limit block 23, and the second limit block 23 is always stationary; one end of the second transmission shaft 13 close to the connecting plate 3 always abuts against the second limit block 23; the second limit block 23 is a two-thirds sector, and the central angle of the second limit block 23 is 240°. The meshing track 102 of the front positioning track 101 of the semi-toothed ring 1 is opposite to the sector-shaped recessed part of the second limit block 23, and the disengagement track 103 of the front positioning track 101 of the semi-toothed ring 1 is opposite to the sector-shaped protrusion of the second limit block 23; when the second transmission shaft 13 abuts against the sector-shaped recessed part of the second limit block 23, the second power gear 7 corresponding to the second transmission shaft 13 is located at the semi-toothed ring 1 In the meshing track 102 of the front positioning track 101, the second power gear 7 is meshed with the half-toothed ring 1, and the second rotating gear 15 corresponding to the second transmission shaft 13 is meshed with the fourth output gear 17; when the second transmission shaft 13 abuts against the fan-shaped protrusion of the second limit block 23, the second power gear 7 corresponding to the second transmission shaft 13 is located in the meshing track 102 or the disengagement track 103 of the front positioning track 101 of the half-toothed ring 1, the second power gear 7 is meshed with or disengaged from the half-toothed ring 1, and the second rotating gear 15 corresponding to the second transmission shaft 13 is disengaged from the fourth output gear 17; the second limit block 23 is used to ensure that at each moment, only one second rotating gear 15 is meshed with the fourth output gear 17.The first limit block 22 and the second limit block 23 are respectively located on the front and back sides of the half-toothed ring 1, and the two are opposite and identical. The first limit block 22, the second limit block 23, and the positioning track 101 cooperate with each other to ensure that at any time, only one first power gear 6 is engaged with the half-toothed ring 1, and the first belt gear 14 corresponding to the first power gear 6 is engaged with the third output gear 16; and to ensure that at any time, only one second power gear 7 is engaged with the half-toothed ring 1, and the second belt gear 15 corresponding to the second power gear 7 is engaged with the fourth output gear 17. The first limit block 22 and the second limit block 23 allow the first transmission shaft 12 and the second transmission shaft 13 to reciprocate along the extended diameter of the transmission disk 2 during the circumferential rotation, so that at any time, only one first belt gear 14 and the second belt gear 15 are engaged with the third output gear 16 and the fourth output gear 17, respectively, ensuring that all first belt gears 14 are engaged with the third output gear 16 in turn, and all second belt gears 15 are engaged with the fourth output gear 17 in turn.

[0059] The first speed shift rail 4 and the second speed shift rail 5 are both provided with sliding grooves along the length direction. The first power gear 6 and the first intermediate transmission gear 8 are fixedly connected through the sliding grooves of the first speed shift rail 4 and are respectively located on both sides of the first speed shift rail 4. The second power gear 7 and the second intermediate transmission gear 9 are fixedly connected through the sliding grooves of the second speed shift rail 5 and are respectively located on both sides of the second speed shift rail 5.

[0060] Springs are provided between the first transmission shaft 12 and the first limit block 22 , and between the second transmission shaft 13 and the second limit block 23 to ensure that the end of the first transmission shaft 12 always abuts against the first limit block 22 , and the end of the second transmission shaft 13 always abuts against the second limit block 23 .

[0061] In this embodiment, the half-gear ring 1 is a half-circular ring, ensuring that it does not occupy excessive area during shifting. In another preferred embodiment, the half-gear ring 1 is a full-circular ring, and the positioning track is arranged in a closed loop along the circumference of the half-gear ring 1. The first power gear 6 and the second power gear 7 always move along the positioning track 101, that is, the first slider 601 and the second slider 701 are always embedded in the positioning track 101.

[0062] The principle of this transmission is:

[0063] The driver is started, and the driver drives the transmission disc 2 to rotate axially, and the transmission disc 2 drives the connecting plate 3 to rotate.

[0064] The connecting plate 3 drives the first speed change rail 4 to rotate circumferentially, and the first speed change rail 4 drives the first power gear 6 to move along the positioning track 101 on the front side of the half gear ring 1. When the first power gear 6 moves to the meshing track 102 of the positioning track 101, and the first transmission shaft 12 corresponding to the first power gear 6 abuts against the fan-shaped recessed part of the first limit block 22, the first power gear 6 meshes with the half gear ring 1, and the half gear ring 1 does not rotate. The first power gear 6 moves along the half gear ring 1 and starts to rotate axially, driving the first intermediate gear 8 to rotate axially, the first intermediate gear 8 drives the first transmission gear 10 to rotate axially, the first transmission gear 10 drives the first transmission shaft 12 to rotate axially, the first transmission shaft 12 drives the first belt gear 14 to rotate axially, the first belt gear 14 drives the third output gear 16 to rotate axially, and the third output gear 16 drives the first output gear 18 to rotate axially;

[0065] At the same time, the connecting plate 3 drives the transmission plate 24 to rotate circumferentially, and the transmission plate 24 drives the second speed-changing rail 5 to rotate circumferentially. The second speed-changing rail 5 drives the second power gear 7 to move along the positioning track 101 on the back of the half gear ring 1. The second power gear 7 moves to the meshing track 102 of the positioning track 101, and when the second transmission shaft 13 corresponding to the second power gear 7 abuts against the fan-shaped recessed part of the second limit block 23, the second power gear 7 meshes with the half gear ring 1, and the half gear ring 1 does not rotate. The second power gear 7 moves along the half gear ring 1 and starts to rotate axially, driving the second intermediate gear 9 to rotate axially. The second intermediate gear 9 drives the second transmission gear 11 to rotate axially. The second transmission gear 11 drives the second transmission shaft 13 to rotate axially. The second transmission shaft 13 drives the second belt rotating gear 15 to rotate axially. The second belt rotating gear 15 drives the fourth output gear 17 to rotate axially. The fourth output gear 17 drives the second output gear 19 to rotate axially.

[0066] The first output gear 18 and the second output gear 19 drive the differential gear 20 to rotate axially and circumferentially. The speeds of the first output gear 18 and the second output gear 19 are neutralized by the differential gear 20 and transmitted to the differential gear 20. The final rotational speed is transmitted by the differential gear 20 to the output shaft 21 for output.

[0067] At each moment, on the front of the semi-toothed ring 1, only one first power gear 6 corresponding to the first speed shift rail 4 is meshed with the semi-toothed ring 1, and the first belt gear 14 corresponding to the first speed shift rail 4 is meshed with the third output gear 16. At the same time, on the back of the semi-toothed ring 1, only one second power gear 7 corresponding to the second speed shift rail 5 is meshed with the semi-toothed ring 1, and the second belt gear 15 corresponding to the second speed shift rail 5 is meshed with the fourth output gear 17. That is, at each moment, only one first belt gear 14 and one second belt gear 15 are respectively meshed with the third output gear 16 and the fourth output gear 17. At each moment, the third output gear 16 and the fourth output gear 17 are respectively driven by one first belt gear 14 and one second belt gear 15; the first speed shift rail 4 and the second speed shift rail 5 are respectively located on two adjacent connecting plates 3.

[0068] The speed shifting principle of this transmission is:

[0069] Move the half gear ring 1 to change the distance between the half gear ring 1 and the transmission plate 2;

[0070] The half-gear ring 1 drives the first power gear 6 to slide along the first speed-changing rail 4, and the distance between the first power gear 6 and the transmission plate 2 changes. When the first power gear 6 moves to the meshing track 102 of the positioning track 101 on the front of the half-gear ring 1, the moving speed of the first power gear 6 changes. Then, through the principle of the above-mentioned transmission, the speed transmitted to the first output gear 18 changes.

[0071] At the same time, the half-gear ring 1 drives the second power gear 7 to slide along the second speed-changing rail 5, and the distance between the second power gear 7 and the transmission plate 2 changes. When the second power gear 7 moves to the meshing track 102 of the positioning track 101 on the front of the half-gear ring 1, the moving speed of the second power gear 7 changes. Then, through the principle of the above-mentioned transmission, the speed transmitted to the second output gear 19 changes.

[0072] The speeds of the first output gear 18 and the second output gear 19 change, so that the speed neutralized by the differential gear 20 changes, thereby changing the speed output by the output shaft 21.

[0073] A first power gear 6 moves on the meshing track 102 of the positioning track 101 on the front of the half gear ring 1. At the same time, an adjacent second power gear 7 moves on the meshing track 102 of the positioning track 101 on the back of the half gear ring 1. If the distance between the first power gear 6 and the transmission disc 2 changes from large to small and then large again, the distance between the second power gear 7 and the transmission disc 2 changes from small to large and then small again. Conversely, if the distance between the first power gear 6 and the transmission disc 2 changes from small to large and then small, the distance between the second power gear 7 and the transmission disc 2 changes from large to small and then large again. The distances of the first power gear 6 and the second power gear 7 relative to the transmission disc 2 change simultaneously.

[0074] The entire transmission is driven by pure gear meshing, eliminating the low maximum torque, slippage, and lack of power typically associated with continuously variable transmissions. This ensures smooth and stable power transmission during operation. Gear meshing also allows for power transmission in different rotational directions.

[0075] This transmission achieves speed change directly by changing the working radius. Since the position of the half-toothed ring 1 is not restricted, it has infinite radii and infinite gears. The speed range of speed change is not restricted. Speed ​​change can be achieved by slowly and evenly moving the half-toothed ring 1, ensuring that there is no sense of jerk when shifting. There is no need to directly change the diameter of the meshing gear like the existing transmission, which can be more stable.

[0076] The first power gear 6 and the second power gear 7 always move along the positioning track 101, and the positioning track 101 limits the movement trajectory of the first power gear 6 and the second power gear 7; when the half gear ring 1 changes its position, the positioning track 101 is used to prevent the first power gear 6 and the second power gear 7 from completely disengaging from the half gear ring 1 and being unable to engage with the half gear ring 1.

[0077] The manner in which the plurality of first power gears 6 are alternately meshed with the half gear ring 1 and the manner in which the plurality of second power gears 7 are alternately meshed with the half gear ring 1 ensures smoothness of the speed change during the speed change process.

[0078] The principles and implementation methods of the present invention are described herein using specific embodiments. The description of the above embodiments is intended only to facilitate understanding of the method and core concept of the present invention. It should be noted that those skilled in the art may make various improvements and modifications to the present invention without departing from the principles of the present invention, and such improvements and modifications also fall within the scope of protection of the claims of the present invention.

Claims

1. A transmission, characterized in that: The gear train comprises a first gear and a second gear, and a second gear which is fixedly connected to the gear train, a first gear which is movable along the first gear train and is rotated axially along the gear train, a first transmission shaft which is rotated by the first power gear, and a first output gear which is rotated by the first transmission shaft. The gear train, the first gear train, the first gear train and the first transmission shaft are all located on the front side of the gear train. The gear train also comprises a second gear train which is fixedly connected to the gear train, a second gear which is movable along the second gear train and is rotated axially along the gear train, a second transmission shaft which is rotated by the second power gear, and a second output gear which is rotated by the second transmission shaft. The gear train, the second gear train, the second gear train and the second transmission shaft Both are located on the back of the half-gear ring; the first speed change rail and the second speed change rail are arranged in parallel and staggered, and their rotation paths are the same but they never overlap; a differential gear is engaged between the first output gear and the second output gear to neutralize the speed difference between the two output gears; when changing speed, the half-gear ring is moved to change the distance between the half-gear ring and the transmission plate, and the half-gear ring pushes the first power gear to move along the first speed change rail and the second power gear to move along the second speed change rail. By changing the distance between the first power gear and the second power gear and the transmission plate, the speed of the first power gear and the second power gear meshing with the half-gear ring is changed, thereby changing the rotation speed of the first output gear and the second output gear, and then changing the speed neutralized on the differential gear; A first limit block is fixed on the front of the half-toothed ring. The first limit block is coaxial and concentric with the half-toothed ring. One end of the first transmission shaft abuts against the first limit block. During the circumferential rotation of the first transmission shaft, the end of one end thereof moves along the first limit block. The first limit block is fan-shaped. A second limit block is fixed on the back of the half-toothed ring. The second limit block is coaxial and concentric with the half-toothed ring. One end of the second transmission shaft abuts against the second limit block. During the circumferential rotation of the second transmission shaft, the end of one end thereof moves along the second limit block. The second limit block is fan-shaped. The first power gear is always engaged with a first transmission gear, which is provided on the first transmission shaft and can move along the first transmission shaft. The rotation of the first power gear drives the first transmission gear to rotate, and the first transmission gear drives the first transmission shaft to rotate axially; the second power gear is always engaged with a second transmission gear, which is provided on the second transmission shaft and can move along the second transmission shaft. The rotation of the second power gear drives the second transmission gear to rotate, and the second transmission gear drives the second transmission shaft to rotate axially; A first rotating gear is fixed to one end of the first transmission shaft near the end portion, and the first rotating gear is meshed with a third output gear. The third output gear is coaxial and concentric with the first output gear, and the third output gear drives the first output gear to rotate synchronously. The first transmission shaft rotates axially, driving the first rotating gear to rotate, the first rotating gear drives the third output gear to rotate, and the third output gear drives the first output gear to rotate; A second belt-rotating gear is fixed at a position near the end of one end of the second transmission shaft, and the second belt-rotating gear is meshed with a fourth output gear. The fourth output gear is coaxial and concentric with the second output gear and the fourth output gear drives the second output gear to rotate synchronously. The second transmission shaft rotates axially, driving the second belt-rotating gear to rotate, the second belt-rotating gear drives the fourth output gear to rotate, and the fourth output gear drives the second output gear to rotate; The first power gear and the first transmission gear are meshed with each other through a first intermediate transmission gear. The first intermediate transmission gear and the first power gear are coaxial and concentric, and the two are fixedly connected and rotate synchronously. The first intermediate transmission gear is meshed with the first transmission gear. The second power gear is meshed with the second transmission gear through the second intermediate transmission gear. The second intermediate transmission gear is coaxial and concentric with the second power gear and is fixedly connected and rotates synchronously. The second intermediate transmission gear is meshed with the second transmission gear.

2. The transmission according to claim 1, wherein: The front and back sides of the semi-toothed ring are respectively provided with meshing teeth for engaging the first power gear and the second power gear; the front and back sides of the semi-toothed ring are both provided with positioning tracks along the circumferential direction; the first power gear is axially extended with a first slider, which can be embedded in the positioning track on the front side of the semi-toothed ring and move along the positioning track; the second power gear is axially extended with a second slider, which can be embedded in the positioning track on the back side of the semi-toothed ring and move along the positioning track.

3. The transmission according to claim 1, wherein: At least two first speed change rails are provided on the front side of the half gear ring, and the first power gears on the two first speed change rails are alternately meshed with the half gear ring.

4. The transmission according to claim 3, wherein: At least two second speed change rails are provided on the back of the half gear ring, and the second power gears on the two second speed change rails are alternately meshed with the half gear ring.

5. The transmission according to claim 1, wherein: The differential gear is rotatably connected to an output shaft, the axis of the output shaft is perpendicular to the axis of the differential gear, the output shaft is driven to rotate by the differential gear, and the power of the driver is output through the output shaft.

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