A continuously variable transmission

Abstract

The present invention discloses a continuously variable transmission, belonging to the technical field of transmissions. The continuously variable transmission includes a housing, wherein a first mounting cavity is provided within the housing; a differential, wherein the differential is mounted within the first mounting cavity, with the input end of the differential extending out and a shaft connected to one end of the housing; a planetary reducer, wherein the planetary reducer is mounted within the first mounting cavity, with one end of the planetary reducer connected to the output end of the differential; a hydraulic coupler, wherein the hydraulic coupler is mounted within the first mounting cavity, with one end of the hydraulic coupler connected to the other end of the planetary reducer; and a torque controller, wherein the torque controller is mounted within the first mounting cavity, with one end of the torque controller connected to the other end of the hydraulic coupler, and the other end of the torque controller passes through and extends out of the other end of the housing. The transmission has a strong output capacity, flexible torque conversion, and simple control, and can be used in various working conditions.

Description

Technical Field

[0001] The present invention relates to the technical field of transmissions, and more particularly to a continuously variable transmission. Background Art

[0002] As a core component of an automobile, the transmission primarily changes engine speed and torque. This allows for changing the transmission ratio, enabling reverse driving, or interrupting power transmission. A transmission consists of two main parts: a transmission mechanism and an operating mechanism. The transmission mechanism primarily changes the speed and torque, while the operating mechanism controls the transmission mechanism to achieve a change in transmission ratio. This means shifting gears to achieve torque conversion.

[0003] Currently used transmissions include manual transmissions (MTs), which are cumbersome to operate, experience noticeable shifting jerks, and require high driver skill. Automatic transmissions (ATs) are complex, require a lot of technical expertise, and have low transmission efficiency and high fuel consumption. Continuously variable transmissions (CVTs) have limited torque capacity on their steel belts, limiting output torque. The belts and pulleys are expensive, leading to high maintenance costs. Summary of the Invention

[0004] The purpose of the present invention is to provide a continuously variable transmission to solve the technical problems existing in the background technology.

[0005] In order to achieve the above object, the present invention adopts the following technical solutions:

[0006] A continuously variable transmission comprises: a housing, wherein a first mounting cavity is provided in the housing; a differential, wherein the differential is mounted in the first mounting cavity, and an input end of the differential extends out and is connected to a shaft at one end of the housing; a planetary reducer, wherein the planetary reducer is mounted in the first mounting cavity, and one end of the planetary reducer is connected to the output end of the differential; a hydraulic coupler, wherein the hydraulic coupler is mounted in the first mounting cavity, and one end of the hydraulic coupler is connected to the other end of the planetary reducer; and a torque controller, wherein the torque controller is mounted in the first mounting cavity, and one end of the torque controller is connected to the other end of the hydraulic coupler, and the other end of the torque controller passes through and extends out of the other end of the housing.

[0007] Furthermore, the differential includes: a first input shaft, a first bearing, a first planetary carrier, a first meshing transmission component, a second bearing and a connecting shaft, one end of the first input shaft passes through and extends out of one end of the housing, the other end of the first input shaft is connected to the first planetary carrier, the first meshing transmission component is arranged on the first planetary carrier, one end of the connecting shaft is connected to the first meshing transmission component, and the other end of the connecting shaft passes through the planetary reducer and is connected to the second bearing arranged on the industrial hydraulic coupler.

[0008] Furthermore, the first meshing transmission component includes a first planetary gear and a second planetary gear arranged opposite to each other; a first bevel gear and a second bevel gear arranged opposite to each other, the first planetary carrier includes an upper mounting end and a lower mounting end, and a placement cavity is formed between the upper mounting end and the lower mounting end, the first planetary gear shaft is connected to the upper mounting end, and the second planetary gear shaft is connected to the lower mounting end, the first bevel gear is arranged in the placement cavity, one end of the connecting shaft is fixedly connected to the first bevel gear, and the second bevel gear is provided with an avoidance cavity passing through it in the axial direction, the second bevel gear is connected to the end of the planetary reducer, and the connecting shaft passes through the avoidance cavity, the first planetary gear is respectively meshed with the first bevel gear and the second bevel gear, and the second planetary gear is respectively meshed with the first bevel gear and the second bevel gear.

[0009] Furthermore, the planetary reducer includes an inner ring gear and a second meshing transmission component, a second mounting cavity is opened inside the inner ring gear, one end of the inner ring gear is a closed end, and the other end of the inner ring gear is an open end, a through hole for the connecting shaft to pass through is opened on the closed end, the second meshing transmission component is arranged in the second mounting cavity, the connecting shaft passes through the second meshing transmission component, and the second meshing transmission component is meshed with the inner wall of the second mounting cavity; the open end is connected to the end face of the hydraulic coupler.

[0010] Furthermore, the second meshing transmission component includes a first-stage reduction gear set, a second-stage reduction gear set, a third-stage reduction gear set, a second planetary carrier, a third planetary carrier, a fourth planetary carrier and a cam. The first-stage reduction gear set is fixedly connected to the connecting shaft. The first-stage reduction gear set transmits power to the second-stage reduction gear set through the second planetary carrier. The second-stage reduction gear set transmits power to the third-stage reduction gear set through the third planetary carrier. The third-stage reduction gear set transmits power to the cam through the fourth planetary carrier.

[0011] Furthermore, the hydraulic coupler includes: a mounting plate, a first partition plate is provided in the mounting plate, the first partition plate divides the mounting plate into an inner mounting cavity and an outer mounting cavity that are sealed from each other, a plurality of oil cylinders arranged at equal intervals are installed in the outer mounting cavity, the telescopic end seal of the oil cylinder passes through the first partition plate and is arranged in the inner mounting cavity, the cam is arranged in the inner mounting cavity, and when the cam rotates, it contacts the telescopic end of each oil cylinder respectively, and the inner gear ring is connected to the inner mounting cavity.

[0012] Furthermore, the hydraulic coupler also includes an annular oil guide pipe and an oil return pipe. The oil outlet pipe of each oil cylinder passes through the side wall of the external mounting cavity and is connected to the annular oil guide pipe arranged outside the external mounting cavity. One end of the return oil pipe is connected to the annular oil guide pipe, and the other end of the return oil pipe is connected to the side wall of the external mounting cavity, and the return oil pipe passes through the torque controller.

[0013] Furthermore, the torque controller includes a first coupler output shaft and a second coupler output shaft, a second partition plate is provided in the shell, one end of the first coupler output shaft passes through the second partition plate and is connected to the mounting plate, the first coupler output shaft and the second partition plate are connected by a third bearing, a third mounting cavity is opened at one end of the second coupler output shaft, the other end of the first coupler output shaft is screwed into the third mounting cavity, and the end of the third mounting cavity is slidingly sealed with the first coupler output shaft through the end cover, a fourth mounting cavity connected to the third mounting cavity is axially provided in the first coupler output shaft, the return oil pipe passes through and is connected to the fourth mounting cavity, a pin assembly for connecting and blocking the return oil pipe is provided in the fourth mounting cavity, the pin assembly sliding seal is provided in the fourth mounting cavity, a gap is reserved between the end faces of the first coupler output shaft and the third mounting cavity, and the gap is filled with hydraulic oil.

[0014] Furthermore, the oil return pipe includes an upper oil pipe and a lower oil pipe, one end of the upper oil pipe is connected to the outer mounting cavity, the other end of the upper oil pipe is connected to the fourth mounting cavity, one end of the lower oil pipe is connected to the fourth mounting cavity, and is arranged opposite to the other end of the upper oil pipe, and the other end of the lower oil pipe is connected to the annular oil guide pipe.

[0015] Furthermore, the ejector pin assembly includes a first spring, a first ejector pin, a second ejector pin and a second spring. The fourth mounting cavity includes a sliding cavity and a locking cavity that are interconnected. The diameter of the locking cavity is larger than that of the sliding cavity. The first spring is arranged to abut against the end of the sliding cavity. The first ejector pin abuts against the first spring and is arranged in the sliding cavity. An annular groove section is provided on the first ejector pin. The diameter of the first ejector pin is the same as that of the sliding cavity. The second ejector pin is T-shaped. One end of the second ejector pin abuts against the first ejector pin and is arranged in the sliding cavity. The other end of the second ejector pin is arranged in the locking cavity and is slidably sealed with the locking cavity. The second spring is sleeved on the second ejector pin in the locking cavity.

[0016] Compared with the prior art, the present invention has the following beneficial effects:

[0017] This invention boasts a novel structure and strong practicality. The continuously variable transmission provided by this invention adapts the input power to varying speeds and torques without interrupting transmission, providing tailored power transmission for different operating conditions. It offers excellent compatibility with the engine, ensuring optimal engine operation and improving fuel economy. Gear wear is minimized during extended high-speed output, extending service life. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Figure 1 It is a schematic diagram of a continuously variable transmission of the present invention.

[0019] Figure 2 It is an internal schematic diagram of a continuously variable transmission of the present invention.

[0020] Figure 3 It is a structural schematic diagram of a continuously variable transmission of the present invention.

[0021] Figure 4 It is a structural schematic diagram of a differential of a continuously variable transmission of the present invention.

[0022] Figure 5 It is a structural schematic diagram of a planetary reducer of a continuously variable transmission of the present invention.

[0023] Figure 6 It is a structural schematic diagram of the second meshing transmission component of a planetary reducer of a continuously variable transmission of the present invention.

[0024] Figure 7 It is a structural schematic diagram of a hydraulic joint of a continuously variable transmission from a first perspective of the present invention.

[0025] Figure 8 It is a structural schematic diagram of a hydraulic joint of a continuously variable transmission from a second perspective of the present invention.

[0026] Figure 9 It is a structural schematic diagram of the connection between a hydraulic coupling and a torque controller of a continuously variable transmission of the present invention.

[0027] Figure 10 It is a structural schematic diagram of a first ejector pin of a continuously variable transmission of the present invention.

[0028] Figure 11 It is a structural schematic diagram of the output shaft of the first coupler of a continuously variable transmission of the present invention.

[0029] Figure 12 It is a structural schematic diagram of the second coupler output shaft of a continuously variable transmission of the present invention.

[0030] Markings in the figure: 1-first input shaft, 2-first planetary carrier, 3-first bevel gear, 4-first planetary gear, 5-second planetary gear, 6-second bevel gear, 7-sun gear of the first-stage reduction gear set, 8-planetary gear of the first-stage reduction gear set, 9-second planetary carrier, 10-planetary gear of the second-stage reduction gear set, 11-sun gear of the second-stage reduction gear set, 12-third planetary carrier, 13-inner ring gear, 14-cam, 15-oil cylinder, 16-piston rod, 17-first bearing, 18-second coupler output shaft, 19-housing, 20-differential, 21-connecting shaft, 22-second bearing, 23-sun gear of the third-stage reduction gear set, 24-third-stage reduction gear Planetary gears of the wheel set, 25-fourth planetary carrier, 26-annular oil guide pipe, 27-first spring, 28-first ejector pin, 29-second ejector pin, 30-second spring, 31-oil seal, 32-brake wheel, 33-first coupler output shaft, 34-third bearing, 35-shifter, 36-planetary reducer, 37-hydraulic coupler, 38-torque controller, 39-first stage reduction gear set, 40-second stage reduction gear set, 41-third stage reduction gear set, 42-end cover, 43-first partition plate, 44-return oil pipe, 45-external mounting cavity, 46-inner mounting cavity, 47-latch, 48-upper oil pipe, 49-lower oil pipe, 50-annular groove segment. DETAILED DESCRIPTION

[0031] The present invention will be further described below with reference to the embodiments. The embodiments described are only a part of the embodiments of the present invention and are not all embodiments. Based on the embodiments of the present invention, other embodiments obtained by ordinary technicians in this field without making creative work are all within the scope of protection of the present invention.

[0032] Embodiment 1:

[0033] like Figure 1-3 As shown, a continuously variable transmission includes: a housing 19, wherein a first mounting cavity is provided in the housing 19; a differential 20, wherein the differential 20 is mounted in the first mounting cavity, and the input end of the differential 20 extends and the shaft is connected to one end of the housing 19; a planetary reducer 36, wherein the planetary reducer 36 is mounted in the first mounting cavity, and one end of the planetary reducer 36 is connected to the output end of the differential 20; a hydraulic coupler 37, wherein the hydraulic coupler 37 is mounted in the first mounting cavity, and one end of the hydraulic coupler 37 is connected to the other end of the planetary reducer 36; a torque controller 38, wherein the torque controller 38 is mounted in the first mounting cavity, and one end of the torque controller 38 is connected to the other end of the hydraulic coupler 37, and the other end of the torque controller 38 passes through and extends out of the other end of the housing 19.

[0034] like Figure 4As shown, in this embodiment, the differential 20 includes: a first input shaft 1, a first bearing 17, a first planetary carrier 2, a first meshing transmission component, a second bearing 22 and a connecting shaft 21. One end of the first input shaft 1 passes through and extends out of one end of the housing 19, and the other end of the first input shaft 1 is connected to the first planetary carrier 2. The first meshing transmission component is provided on the first planetary carrier 2. One end of the connecting shaft 21 is connected to the first meshing transmission component, and the other end of the connecting shaft 21 passes through the planetary reducer 36 and is connected to the second bearing 22 provided on the hydraulic coupler 37.

[0035] In this embodiment, the first meshing transmission component includes a first planetary gear 4 and a second planetary gear 5 arranged opposite to each other; a first bevel gear 3 and a second bevel gear 6 arranged opposite to each other, the first planetary carrier 2 includes an upper mounting end and a lower mounting end, and a placement cavity is formed between the upper mounting end and the lower mounting end, the first planetary gear 4 is axially connected to the upper mounting end, and the second planetary gear 5 is axially connected to the lower mounting end, the first bevel gear 3 is arranged in the placement cavity, one end of the connecting shaft 21 is fixedly connected to the first bevel gear 3, and the second bevel gear 6 is axially provided with a penetrating avoidance cavity, the second bevel gear 6 is connected to the end of the planetary reducer 36, and the connecting shaft 21 is arranged to pass through the avoidance cavity, the first planetary gear 4 is respectively meshed with the first bevel gear 3 and the second bevel gear 6, and the second planetary gear 5 is respectively meshed with the first bevel gear 3 and the second bevel gear 6.

[0036] First input shaft 1 transmits input power to first planet carrier 2. This power is then distributed to first bevel gear 3 and second bevel gear 6 via first planetary gears 4 and 5 mounted on first planetary gear carrier 2. Second bevel gear 6 is rigidly connected to ring gear 13, and ring gear 13 is rigidly connected to first coupler output shaft 33. In other words, the power distributed to second bevel gear 6 reaches first coupler output shaft 33 directly.

[0037] One end of the first input shaft 1 is rigidly connected to the first bevel gear 3, while the other end passes through the clearance cavity of the second bevel gear 6, the second meshing transmission component, and the opening of the cam 14, and is fixed to the second bearing 22. The sun gear 7 of the primary reduction gear set is rigidly connected and fixed to the first input shaft 1. In this way, the power from the first bevel gear 3 is transmitted to the sun gear 7 of the primary reduction gear set via the first input shaft 1. The sun gear 7 of the primary reduction gear set then transmits the power to the planet gears 8 of the primary reduction gear set. The planet gears 8 of the primary reduction gear set transmit the power to the second planet carrier 9. The sun gears 11 of the secondary reduction gear set, which are rigidly fastened to the second planet carrier 9, transmit the power to the next set of planet gears, namely, the planet gears 10 of the secondary reduction gear set. The planet gears 10 of the secondary reduction gear set transmit the power to the third planet carrier 12. The third planet carrier 12 transmits the power to the next set of planet gears, namely, the planet gears 24 of the third reduction gear set, via the sun gears 23 of the third reduction gear set, which are rigidly fastened to the third planet carrier 12. The planet gears 24 of the third reduction gear set transmit the power to the fourth planet carrier 25, which in turn transmits the power to the cam 14.

[0038] The power is decelerated by the three-stage planetary reduction gear set and finally transmitted to the cam 14. The reduction ratio of the single-stage reduction gear set is generally 1:2.5 to 1:5. Calculated at 1:5, the reduction ratio after the three-stage planetary reduction gear set is 1:125, thereby achieving the purpose of reducing the speed and increasing the torque.

[0039] like Figure 5-6 As shown, in this embodiment, the planetary reducer 36 includes an inner ring gear 13 and a second meshing transmission component, and a second mounting cavity is opened inside the inner ring gear 13. One end of the inner ring gear 13 is a closed end, and the other end of the inner ring gear 13 is an open end. A through hole for the connecting shaft 21 to pass through is opened on the closed end. The second meshing transmission component is arranged in the second mounting cavity, and the connecting shaft 21 passes through the second meshing transmission component, and the second meshing transmission component is meshed with the inner wall of the second mounting cavity; the open end is connected to the end face of the hydraulic coupler 37.

[0040] In this embodiment, the second meshing transmission component includes a first-stage reduction gear set 39, a second-stage reduction gear set 40, a third-stage reduction gear set 41, a second planetary carrier 9, a third planetary carrier 12, a fourth planetary carrier 25 and a cam 14. The first-stage reduction gear set 39 is fixedly connected to the connecting shaft 21. The first-stage reduction gear set 39 transmits power to the second-stage reduction gear set 40 through the second planetary carrier 9. The second-stage reduction gear set 40 transmits power to the third-stage reduction gear set 41 through the third planetary carrier 12. The third-stage reduction gear set 41 transmits power to the cam 14 through the fourth planetary carrier 25.

[0041] like Figure 7-8As shown, in this embodiment, the hydraulic coupler 37 includes a mounting plate, within which is disposed a first annular partition plate 43. The first annular partition plate 43 divides the mounting plate into a sealed inner mounting chamber 46 and an outer mounting chamber 45. A plurality of oil cylinders 15 are mounted within the outer mounting chamber 45, spaced equidistantly and annularly. The telescopic ends of the oil cylinders 15 are sealed and extend through the first partition plate 43 and disposed within the inner mounting chamber 46. A pulley is disposed on the piston rod 16 of the oil cylinder 15, which facilitates contact with the cam 14. The circular motion of the cam 14 pushes the pulley, which in turn pushes the piston rod 16 of the oil cylinder 15 to reciprocate. The cam 14 is disposed within the inner mounting chamber 46 and, when the cam 14 rotates, contacts the telescopic ends of each oil cylinder 15. The inner gear ring 13 is in communication with the inner mounting chamber 46. When the cam 14 and the telescopic ends of the cylinders 15 of the hydraulic coupler 37 are in a separated state, the power input by the first input shaft 1 is affected by the resistance of the output end, and the power is automatically distributed to the first bevel gear 3 by the first planetary gear 4 and the second planetary gear 5. After three-stage planetary reduction, the high torque is finally output by the cam 14.

[0042] like Figure 9 As shown, by closing the oil outlet of cylinder 15, the pressure in cylinder 15 increases, which in turn increases the resistance between the pulley of piston rod 16 and cam 14, thus causing the cam 14 to engage with the hydraulic coupler 37. The engagement process is the process of controlling the speed difference between cam 14 and hydraulic coupler 37. In other words, it is the process of converting the input speed into any desired speed input.

[0043] In this embodiment, the hydraulic coupler 37 also includes an annular oil guide pipe 26 and an oil return pipe 44. The oil outlet pipe of each oil cylinder 15 passes through the side wall of the outer mounting cavity 45 and is connected to the annular oil guide pipe 26 arranged outside the outer mounting cavity 45. One end of the return oil pipe 44 is connected to the annular oil guide pipe 26, and the other end of the return oil pipe 44 is connected to the side wall of the outer mounting cavity 45, and the return oil pipe 44 passes through the torque controller 38.

[0044] like Figure 11-12As shown, in this embodiment, the torque controller 38 includes a first coupler output shaft 33 and a second coupler output shaft 18. A second partition plate is provided within the housing 19. One end of the first coupler output shaft 33 passes through the second partition plate and is connected to the mounting plate. The first coupler output shaft 33 and the second partition plate are connected via a third bearing 34. A third mounting cavity is defined at one end of the second coupler output shaft 18. The other end of the first coupler output shaft 33 is threaded within the third mounting cavity, and a sliding seal is achieved between the end cap 42 and the first coupler output shaft 33. Specifically, an oil seal 31 is provided between the end cap 42 and the first coupler output shaft 33. The other end of the second coupler output shaft 18 passes through and extends out of a shifter 35 provided within the housing 19. The second coupler output shaft 18 is gear-connected to the shifter 35 to achieve switching between forward and reverse gears.

[0045] A fourth mounting cavity connected to the third mounting cavity is axially provided in the first coupler output shaft 33, and the return oil pipe 44 passes through and is connected to the fourth mounting cavity. A ejector assembly for connecting and blocking the return oil pipe 44 is provided in the fourth mounting cavity. The ejector assembly is slidingly sealed in the fourth mounting cavity. A gap is reserved between the end faces of the first coupler output shaft 33 and the third mounting cavity, and the gap is filled with hydraulic oil.

[0046] In this embodiment, the oil return pipe 44 includes an upper oil pipe 48 and a lower oil pipe 49. One end of the upper oil pipe 48 is connected to the outer mounting cavity 45, and the other end of the upper oil pipe 48 is connected to the fourth mounting cavity. One end of the lower oil pipe 49 is connected to the fourth mounting cavity and is arranged opposite to the other end of the upper oil pipe 48. The other end of the lower oil pipe 49 is connected to the annular oil guide pipe 26.

[0047] like Figure 10 As shown, in this embodiment, the ejector pin assembly includes a first spring 27, a first ejector pin 28, a second ejector pin 29 and a second spring 30. The fourth mounting cavity includes a sliding cavity and a locking cavity that are interconnected. The diameter of the locking cavity is larger than that of the sliding cavity. The first spring 27 is arranged against the end of the sliding cavity, and the first ejector pin 28 is arranged in the sliding cavity against the first spring 27. An annular groove section 50 is provided on the first ejector pin 28. The diameter of the first ejector pin 28 is the same as that of the sliding cavity. The second ejector pin 29 is T-shaped. One end of the second ejector pin 29 is arranged in the sliding cavity against the first ejector pin 28, and the other end of the second ejector pin 29 is arranged in the locking cavity and is slidably sealed with the locking cavity. The second spring 30 is sleeved on the second ejector pin 29 in the locking cavity.

[0048] When the first ejector pin 28 is arranged in the sliding cavity and blocks the upper oil pipe 48 and the lower oil pipe 49, the oil circuit of the oil cylinder 15 is blocked. Therefore, the cam 14 is positioned by the pulley at the end of the piston rod 16 of each oil cylinder 15. The differential 20, the planetary reducer 36, the hydraulic coupler 37 and the torque controller 38 are a whole. The gear structures inside each of them will not rotate. The power input from the first output shaft is all output from the second coupler output shaft 18 of the torque controller 38 at a 1:1 ratio.

[0049] When the resistance of second coupler output shaft 18 increases, causing its speed to decrease, driving the speed of first coupler output shaft 33 down. Due to inertia, first coupler output shaft 33, which is threadedly connected to it, continues to rotate at a high speed relative to it, and thus moves toward second coupler output shaft 18. At this point, the space between first coupler output shaft 33 and the sidewall of the third mounting cavity begins to decrease. The hydraulic oil within pushes second ejector pin 29 to compress second spring 30, moving it toward first ejector pin 28. This pushes first ejector pin 28 toward first spring 27 and compresses first spring 27. When the annular groove section 50 of first ejector pin 28 connects with upper oil pipe 48 and lower oil pipe 49, the oil outlet passage begins to open, allowing oil to flow back into outer mounting cavity 45. The piston of hydraulic coupler cylinder 15 begins to move, and cam 14 begins to rotate, widening the speed difference with ring gear 13. The torque of first coupler output shaft 33 increases, reaching the same level as that of second coupler output shaft 18. The greater the resistance encountered by the second coupler output shaft 18, the greater the stroke of the first ejector pin 28, and the greater the proportion of the oil outlet opening. The greater the torque matched by the hydraulic coupler 37 to the second coupler output shaft 18. This process automatically adjusts to the resistance encountered by the vehicle during operation.

[0050] The brake wheel 32 is mounted on the first coupler output shaft 33 via a latch 47. The brake wheel 32 and the first ejector pin 28 are linked together. A keyway for this linkage is defined on the first coupler output shaft 33, and the latch 47 is positioned between the first ejector pin 28 and the second ejector pin 29. During braking, the first ejector pin 28 is pushed toward the first spring 27, fully opening the oil passage between the upper and lower oil pipes 48, 49 of the oil outlet. This allows the piston rod 16 of the oil cylinder 15 to repeatedly flow in and out of oil, driven by the cam 14. Power from the first input shaft 1 is automatically transmitted via the first bevel gear 3 to the no-load output of the cam 14, completing the power cut.

[0051] The key point of this invention is the use of differential 20 to split the input power into two groups. The first group is transmitted via the second bevel gears 6 to the ring gear 13 of the planetary reducer 36. This is then transferred to the mounting plate of the hydraulic coupler 37. The second bevel gears 6, the ring gear 13 of the planetary reducer 36, and the mounting plate of the hydraulic coupler 37 are rigidly connected, directly inputting the torque controller input and outputting it. The second group is transmitted via the first bevel gears 3 to the sun gear 7 of the primary reduction gear set. After being shifted by the planetary gears 8 of the primary reduction gear set, it is then decelerated through the third reduction gear set 41 and transferred to the cam 14. When the return oil pipe 44 at the oil outlet of the hydraulic coupler 37 is fully open, the resistance at the power output acts on the ring gear 13, and the second bevel gears 6 of the differential 20 are stationary. All the input power is reduced in speed from the first bevel gears 3 through the planetary reducer 36 to the cam 14 for high-torque no-load output.

[0052] As return line 44 slowly closes under the action of first ejector pin 28, the oil passageway at the outlet of hydraulic coupler 37 begins to narrow, the pressure within cylinder 15 begins to increase, and friction begins to form between cam 14 and the pulley of hydraulic coupler 37's cylinder 15. Cam 14 then drives the output of hydraulic coupler 37 and the output of ring gear 13 to rotate in the same direction, and power output begins. When the proportional increase in resistance caused by closing return line 44 reaches the maximum speed ratio of planetary reducer 36, the output torque of torque controller 38 reaches its maximum. As return line 44 continues to close, the speed difference between hydraulic coupler 37 and cam 14 decreases, the torque at the output of torque controller 38 begins to decrease, and the speed increases. When return line 44 is completely closed, hydraulic coupler 37 and cam 14 lock, and the gears of planetary reducer 36 and differential 20 all lock, and the output speed of torque controller 38 reaches its maximum. The input and output transmission ratio of 1:1 sets the torque value of the torque controller 38 to start the ejector assembly to connect to the oil return pipe 44 to the optimal torque value that matches the engine.

[0053] When the vehicle begins to climb a slope or the forward resistance reaches the engine's optimal torque value, the torque controller 38 activates, pushing the ejector assembly to release pressure from the hydraulic coupler 37's cylinder 15, increasing the speed difference between the hydraulic coupler 37 and the cam 14. This process gains torque at the expense of rotational speed. This process varies with the resistance encountered by the vehicle, thus ensuring that the engine always operates at its optimal level.

[0054] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions and improvements made within the spirit and principles of the present invention should be included in the scope of protection of the present invention.

Claims

1. A continuously variable transmission, characterized in that: include: A housing (19), wherein a first mounting cavity is provided in the housing (19); A differential (20), the differential (20) being installed in the first installation cavity, the input end of the differential (20) extending out and the shaft being connected to one end of the housing (19); A planetary reducer (36), the planetary reducer (36) being installed in the first installation cavity, and one end of the planetary reducer (36) being connected to the output end of the differential (20); a hydraulic coupler (37), wherein the hydraulic coupler (37) is installed in the first installation cavity, and one end of the hydraulic coupler (37) is connected to the other end of the planetary reducer (36); a torque controller (38), wherein the torque controller (38) is installed in the first installation cavity, and one end of the torque controller (38) is connected to the other end of the hydraulic coupler (37), and the other end of the torque controller (38) passes through and extends out of the other end of the housing (19); The differential (20) comprises: a first input shaft (1), a first bearing (17), a first planetary carrier (2), a first meshing transmission component, a second bearing (22) and a connecting shaft (21), one end of the first input shaft (1) passes through and extends out of one end of the housing (19), the other end of the first input shaft (1) is connected to the first planetary carrier (2), the first meshing transmission component is arranged on the first planetary carrier (2), one end of the connecting shaft (21) is connected to the first meshing transmission component, and the other end of the connecting shaft (21) passes through the planetary reducer (36) and is connected to the second bearing (22) arranged on the hydraulic coupler (37); The planetary reducer (36) includes an inner gear ring (13) and a second meshing transmission component, a second mounting cavity is provided inside the inner gear ring (13), one end of the inner gear ring (13) is a closed end, and the other end of the inner gear ring (13) is an open end, a through hole for a connecting shaft (21) to pass through is provided on the closed end, the second meshing transmission component is arranged in the second mounting cavity, the connecting shaft (21) passes through the second meshing transmission component, and the second meshing transmission component is meshed with the inner wall of the second mounting cavity; the open end is connected to the end face of the hydraulic coupler (37); The second meshing transmission component comprises a first-stage reduction gear set (39), a second-stage reduction gear set (40), a third-stage reduction gear set (41), a second planetary carrier (9), a third planetary carrier (12), a fourth planetary carrier (25) and a cam (14); the first-stage reduction gear set (39) is fixedly connected to the connecting shaft (21); the first-stage reduction gear set (39) transmits power to the second-stage reduction gear set (40) through the second planetary carrier (9); the second-stage reduction gear set (40) transmits power to the third-stage reduction gear set (41) through the third planetary carrier (12); and the third-stage reduction gear set (41) transmits power to the cam (14) through the fourth planetary carrier (25); The hydraulic coupler (37) comprises: a mounting plate, a first partition plate (43) is provided in the mounting plate, the first partition plate (43) divides the mounting plate into an inner mounting cavity (46) and an outer mounting cavity (45) which are sealed from each other, a plurality of oil cylinders (15) arranged at equal intervals are installed in the outer mounting cavity (45), the telescopic ends of the oil cylinders (15) are sealed and pass through the first partition plate (43) and are arranged in the inner mounting cavity (46), the cam (14) is arranged in the inner mounting cavity (46), and when the cam (14) rotates, it contacts the telescopic ends of each oil cylinder (15), and the inner gear ring (13) and the inner mounting cavity (46) are connected; The first meshing transmission component includes a first planetary gear (4) and a second planetary gear (5) that are relatively arranged; a first bevel gear (3) and a second bevel gear (6) that are relatively arranged; the first planetary carrier (2) includes an upper mounting end and a lower mounting end, and a placement cavity is formed between the upper mounting end and the lower mounting end; the first planetary gear (4) is axially connected to the upper mounting end; the second planetary gear (5) is axially connected to the lower mounting end; the first bevel gear (3) is arranged in the placement cavity; one end of the connecting shaft (21) is fixedly connected to the first bevel gear (3); the second bevel gear (6) is provided with an axially penetrating avoidance cavity; the second bevel gear (6) is connected to the end of the planetary reducer (36); the connecting shaft (21) is arranged to penetrate the avoidance cavity; the first planetary gear (4) is respectively meshed with the first bevel gear (3) and the second bevel gear (6); the second planetary gear (5) is respectively meshed with the first bevel gear (3) and the second bevel gear (6).

2. A continuously variable transmission according to claim 1, characterized in that: The hydraulic coupler (37) further includes an annular oil guide pipe (26) and an oil return pipe (44). The oil outlet pipe of each oil cylinder (15) passes through the side wall of the outer mounting cavity (45) and is connected to the annular oil guide pipe (26) arranged outside the outer mounting cavity (45). One end of the oil return pipe (44) is connected to the annular oil guide pipe (26), and the other end of the oil return pipe (44) is connected to the side wall of the outer mounting cavity (45). The oil return pipe (44) passes through the torque controller (38).

3. A continuously variable transmission according to claim 2, characterized in that: The torque controller (38) includes a first coupler output shaft (33) and a second coupler output shaft (18). A second partition plate is provided in the housing (19). One end of the first coupler output shaft (33) passes through the second partition plate and is connected to the mounting plate. The first coupler output shaft (33) and the second partition plate are connected via a third bearing (34). A third mounting cavity is provided at one end of the second coupler output shaft (18). The other end of the first coupler output shaft (33) is screwed into the third mounting cavity, and the end of the third mounting cavity is A sliding seal is achieved between the end cover (42) and the first coupler output shaft (33), a fourth installation cavity connected to the third installation cavity is axially provided in the first coupler output shaft (33), the return oil pipe (44) passes through and is connected to the fourth installation cavity, a thimble assembly for connecting and blocking the return oil pipe (44) is provided in the fourth installation cavity, the thimble assembly sliding seal is provided in the fourth installation cavity, a gap is reserved between the end face of the first coupler output shaft (33) and the third installation cavity, and the gap is filled with hydraulic oil.

4. A continuously variable transmission according to claim 3, characterized in that: The oil return pipe (44) includes an upper oil pipe (48) and a lower oil pipe (49). One end of the upper oil pipe (48) is connected to the outer mounting cavity (45), and the other end of the upper oil pipe (48) is connected to the fourth mounting cavity. One end of the lower oil pipe (49) is connected to the fourth mounting cavity and is arranged opposite to the other end of the upper oil pipe (48). The other end of the lower oil pipe (49) is connected to the annular oil guide pipe (26).

5. A continuously variable transmission according to claim 4, characterized in that: The ejector assembly includes a first spring (27), a first ejector pin (28), a second ejector pin (29) and a second spring (30). The fourth installation cavity includes a sliding cavity and a locking cavity that are interconnected. The diameter of the locking cavity is larger than that of the sliding cavity. The first spring (27) is arranged against the end of the sliding cavity. The first ejector pin (28) is arranged in the sliding cavity against the first spring (27). An annular groove section (50) is provided on the first ejector pin (28). The diameter of the first ejector pin (28) is the same as that of the sliding cavity. The second ejector pin (29) is T-shaped. One end of the second ejector pin (29) is arranged in the sliding cavity against the first ejector pin (28). The other end of the second ejector pin (29) is arranged in the locking cavity and is slidably sealed with the locking cavity. The second spring (30) is sleeved on the second ejector pin (29) in the locking cavity.

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