Hybrid power transmission based on planet cone pulley

Abstract

The utility model provides a hybrid power transmission based on a planet cone pulley. The hybrid power transmission comprises a box body, a driving motor, a clutch and a stepless speed change mechanism, the stepless speed change mechanism comprises an input shaft, a sun bevel gear, three planetary transmission parts, a speed change ring and a planetary support, the input shaft is connected with the driving motor and the clutch at the same time, and power is transmitted to the stepless speed change mechanism to construct the hybrid power transmission; the sun bevel gear and the three planetary transmission parts are combined to form a planetary conical ring type stepless speed change mechanism, so that the transmission speed is adjusted through the displacement of the speed change ring at different positions on the three planetary transmission parts; the variable-speed ring is arranged on the peripheries of the three planetary transmission parts in a sleeving manner, so that transmission is performed through friction force between the inner ring surface of the variable-speed ring and the outer surfaces of the three planetary transmission parts; the speed change ring comprises a speed regulation lead screw and a guide rod, the speed change ring can axially move through the speed regulation lead screw to achieve speed change, and the speed regulation lead screw and the guide rod jointly restrain the circumferential direction of the speed change ring.

Description

Technical Field

[0001] The utility model belongs to the field of transmissions, and particularly relates to a hybrid transmission based on planetary cone wheels. Background Art

[0002] CVT (CONTINUOUSLY VARIABLE TRANSMISSION) technology, i.e., continuously variable transmission technology, uses a transmission belt and driving and driven wheels with variable working diameters to cooperate in transmitting power, and can achieve continuous change of the transmission ratio, thereby obtaining the best match between the transmission system and the engine operating conditions. Common continuously variable transmissions include hydro-mechanical continuously variable transmissions and metal belt continuously variable transmissions (VDT-CVT).

[0003] Currently, the most widely used continuously variable transmission on the market is the mechanical continuously variable transmission, which mostly uses friction transmission methods such as transmission chains, transmission belts or transmission rings. However, the disadvantages of continuously variable transmissions are also obvious. Since most continuously variable transmissions use friction transmission, their transmission components cannot transmit large torques and large loads, and the failure rate caused by friction and wear is relatively high. They cannot be used for high-output power motors and can only be used for vehicles with low power and low torque. Moreover, the production precision of the components of continuously variable transmissions is relatively high, and the cost is also higher than that of ordinary transmissions. Once the transmission belt is damaged, it is relatively troublesome to repair.

[0004] Therefore, how to provide a hybrid special transmission with a new planetary cone-ring type continuously variable transmission mechanism to realize the power coupling of the engine and the motor, and further improve the shift smoothness and transmission efficiency of the hybrid power through the characteristics of continuously variable transmission is a technical problem that those skilled in the art urgently need to solve. Summary of the Utility Model

[0005] The technical problem to be solved by the utility model is to provide a hybrid transmission based on planetary cone wheels to solve at least one of the above technical problems.

[0006] To solve the above technical problems, the present utility model provides a hybrid power transmission based on planetary cone wheels. The hybrid power transmission includes a box body, a driving motor, a clutch, and a continuously variable transmission mechanism. The driving motor and the continuously variable transmission mechanism are both arranged inside the box body. The continuously variable transmission mechanism includes an input shaft, a sun cone gear, three planetary transmission components, a speed change ring, and a planetary bracket. The front end of the input shaft is connected to the box body through a first bearing and is key-connected to the clutch. The middle part of the input shaft is connected to the driving motor. The rear end of the input shaft is key-connected to the sun cone gear. One end of each of the three planetary transmission components is meshed and connected to the sun cone gear, and the three planetary transmission components are symmetrically distributed along the axial direction of the input shaft. The speed change ring is sleeved around the periphery of the three planetary transmission components, so that the outer surfaces of the three planetary transmission components are parallelly abutted against the inner ring surface of the speed change ring. The speed change ring includes a speed regulation lead screw and a guide rod arranged perpendicular to the speed change ring. The speed change ring is threadedly connected to the speed regulation lead screw. Both ends of the speed regulation lead screw and the guide rod are connected to the box body. The two ends of the planetary bracket are respectively connected to the three planetary transmission components and the box body.

[0007] Optionally, the planetary transmission component includes a planetary gear, a planetary wheel shaft, and a speed change cone cylinder. One end of the planetary wheel shaft is fixedly connected to the planetary gear and is connected to one end of the planetary bracket through a second bearing. The planetary gear is meshed and connected to the sun cone gear. The speed change cone cylinder is sleeved around the middle part of the planetary wheel shaft. The other end of the planetary wheel shaft is connected to the other end of the planetary bracket through a third bearing. The outer surface of the speed change cone cylinder is abutted against the inner ring surface of the speed change ring.

[0008] Optionally, the planetary bracket includes a sealing cover, a support frame, and an output shaft. The sealing cover is fixedly connected to one end of the support frame to form a sealed space. The sun cone gear and the three planetary gears are both located inside the sealed space. The rear end of the input shaft passes through the sealing cover and is key-connected to the sun cone gear. The two ends of the support frame are respectively correspondingly connected to the two ends of the three planetary wheel shafts. The middle part of the support frame is distributed in the same axial direction as the input shaft and is located at the center of the three planetary wheel shafts. The other end of the support frame is connected with the output shaft. The output shaft is connected to the box body through a fourth bearing.

[0009] Optionally, the support frame includes a first support disk, a connecting rod, and a second support disk. The centers of the first support disk and the second support disk are respectively fixed to two ends of the connecting rod. The first support disk includes three symmetrically distributed first connecting plates. One end of each of the three planetary gear shafts is respectively connected to one of the three first connecting plates through the second bearing. The second support disk includes three symmetrically distributed second connecting plates. The other end of each of the three planetary gear shafts is respectively connected to one of the three second connecting plates through the third bearing.

[0010] Optionally, the rear end of the input shaft passes through the sealing cover and is connected to the center of the first support disk through a fifth bearing.

[0011] Optionally, the layout plane of any one of the first connecting plates is parallel to the layout plane of any one of the second connecting plates.

[0012] Optionally, a spring pressing mechanism is provided at the connection between the variable speed cone and the planetary gear shaft.

[0013] Optionally, the variable speed ring is provided with a threaded hole and a through hole. The speed regulating screw rod is threadedly connected to the variable speed ring through the threaded hole. The variable speed ring is sleeved on the guide rod through the through hole. Both ends of the guide rod are threadedly connected to the box body.

[0014] Optionally, one end of the speed regulating screw rod is connected to the box body, and the other end of the speed regulating screw rod is connected to a shifting motor. The shifting motor is fixedly installed on the box body.

[0015] Optionally, the first bearing, the second bearing, the third bearing, the fourth bearing, and the fifth bearing are all tapered roller bearings.

[0016] Beneficial effects:

[0017] A hybrid power transmission based on planetary cone wheels provided by the present utility model includes a box body, a drive motor, a clutch, and a continuously variable transmission mechanism. The continuously variable transmission mechanism includes an input shaft, a sun cone gear, three planetary transmission components, a speed change ring, and a planetary bracket. The input shaft is connected to both the drive motor and the clutch at the same time and conducts power to the continuously variable transmission mechanism, thereby constructing a special hybrid power transmission to realize the power coupling of the engine and the motor. The sun cone gear and the three planetary transmission components are combined to construct a planetary cone ring type gear transmission system, so as to adjust the transmission speed by the displacement of the speed change ring at different positions on the three planetary transmission components, realizing the speed change adjustment function. The three planetary transmission components are symmetrically distributed along the axial direction of the input shaft to maintain the stability in the planetary cone ring type gear transmission system and avoid torsion and offset of the planetary transmission components during operation. The speed change ring is sleeved on the periphery of the three planetary transmission components, so that the outer surfaces of the three planetary transmission components are parallel and abutted against the inner ring surface of the speed change ring, and the transmission is carried out through the frictional force between the inner ring surface of the speed change ring and the outer surfaces of the three planetary transmission components. The speed change ring is also provided with a speed adjustment screw rod and a guide rod. The speed change ring can move axially through the speed adjustment screw rod to realize speed change, and the circumferential freedom degree of the speed change ring is jointly restricted by the speed adjustment screw rod and the guide rod. Thus, a special hybrid power transmission with a new planetary cone ring type continuously variable transmission mechanism is constructed to realize the power coupling of the engine and the motor, and further improve the shift smoothness and transmission efficiency of the hybrid power through the characteristics of continuously variable transmission.

[0018] The above description is only an overview of the technical solution of the present utility model. In order to be able to understand the technical means of the present utility model more clearly, it can be implemented according to the content of the description. And in order to make the above and other purposes, features and advantages of the present utility model more obvious and understandable, the following specifically gives the specific embodiments of the present utility model. Brief Description of the Drawings

[0019] In order to more clearly illustrate the technical solutions in the embodiments of this specification or the prior art, the following will briefly introduce the drawings required in the embodiments. Obviously, the drawings in the following description are only some embodiments of the present utility model. For those of ordinary skill in the art, without creative efforts, other drawings can also be obtained based on these drawings.

[0020] Figure 1 It is a cross-sectional view of the hybrid power transmission based on planetary cone wheels provided by the embodiment of the present application;

[0021] Figure 2 It is a three-dimensional view of the overall structure of the hybrid power transmission based on planetary cone wheels provided by the embodiment of the present application;

[0022] Figure 3 It is a front view of the partial structure of the continuously variable transmission mechanism provided by the embodiment of the present application;

[0023] Figure 4 A side view of the partial structure of the continuously variable transmission mechanism provided by the embodiment of the present application;

[0024] Figure 5 A perspective view of the partial structure of the continuously variable transmission mechanism provided by the embodiment of the present application;

[0025] Figure 6 A perspective view of the continuously variable transmission mechanism provided by the embodiment of the present application;

[0026] Figure 7 A front view of the continuously variable transmission mechanism provided by the embodiment of the present application;

[0027] Reference numerals:

[0028] 1 - housing; 2 - drive motor; 3 - clutch; 4 - input shaft; 5 - sun bevel gear; 6 - three planetary transmission parts; 7 - speed change ring; 8 - planetary carrier; 9 - first bearing; 10 - speed regulation lead screw; 11 - guide rod; 12 - planetary gear; 13 - planetary gear shaft; 14 - speed change cone; 15 - second bearing; 16 - third bearing; 17 - sealing cover; 18 - support frame; 19 - output shaft; 20 - fourth bearing; 21 - first support disk; 22 - connecting rod; 23 - second support disk; 24 - first connecting plate; 25 - second connecting plate; 26 - fifth bearing; 27 - spring pressing mechanism; 28 - shift motor; Detailed implementation manners

[0029] Next, the technical solutions in the embodiments of the present utility model will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present utility model. Obviously, the described embodiments are only a part of the embodiments of the present utility model, rather than all the embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative efforts shall fall within the protection scope of the present utility model.

[0030] Please refer to Figures 1-5, this embodiment provides a hybrid transmission based on planetary cone pulleys. The hybrid transmission includes a housing 1, a drive motor 2, a clutch 3, and a continuously variable transmission mechanism. Both the drive motor 2 and the continuously variable transmission mechanism are disposed inside the housing 1; the continuously variable transmission mechanism includes an input shaft 4, a sun cone gear 5, three planetary transmission members 6, a speed change ring 7, and a planetary carrier 8; the front end of the input shaft 4 is connected to the housing 1 through a first bearing 9 and is key-connected to the clutch 3. The middle part of the input shaft 4 is connected to the drive motor 2, and the rear end of the input shaft 4 is key-connected to the sun cone gear 5; one end of each of the three planetary transmission members 6 is meshed and connected to the sun cone gear 5, and the three planetary transmission members 6 are symmetrically distributed along the axial direction of the input shaft 4; the speed change ring 7 is sleeved on the periphery of the three planetary transmission members 6, so that the outer surfaces of the three planetary transmission members 6 are parallel and abutted against the inner ring surface of the speed change ring 7; the speed change ring 7 includes a speed regulation lead screw 10 and a guide rod 11 disposed perpendicular to the speed change ring 7. The speed change ring 7 is threadedly connected to the speed regulation lead screw 10, and both ends of the speed regulation lead screw 10 and the guide rod 11 are connected to the housing 1; both ends of the planetary carrier 8 are respectively connected to the three planetary transmission members 6 and the housing 1.

[0031] Specifically, a hybrid transmission based on planetary cone pulleys provided by the present utility model includes a housing 1, a drive motor 2, a clutch 3, and a continuously variable transmission mechanism. The input shaft in the continuously variable transmission mechanism is simultaneously connected to the drive motor 2 and the clutch 3 (the passive part of the clutch 3), and conducts power to the continuously variable transmission mechanism, thereby constructing a special hybrid transmission to realize the power coupling of the engine and the motor; the sun cone gear 5 and the three planetary transmission members 6 are combined to construct a planetary cone-ring type gear transmission system, so as to adjust the transmission speed by the displacement of the speed change ring 7 at different positions on the three planetary transmission members 6, realizing the speed change adjustment function; the three planetary transmission members 6 are symmetrically distributed along the axial direction of the input shaft 4 to maintain the stability in the planetary cone-ring type gear transmission system and prevent the planetary transmission members 6 from being distorted and offset during operation; the speed change ring 7 is sleeved on the periphery of the three planetary transmission members 6, so that the outer surfaces of the three planetary transmission members 6 are parallel and abutted against the inner ring surface of the speed change ring 7, and the transmission is carried out through the friction force between the inner ring surface of the speed change ring 7 and the outer surfaces of the three planetary transmission members 6; the speed change ring 7 is further provided with a speed regulation lead screw 10 and a guide rod 11. The speed change ring 7 can move axially through the speed regulation lead screw 10 to realize speed change, and the circumferential degree of freedom of the speed change ring 7 is jointly restricted by the speed regulation lead screw 10 and the guide rod 11.

[0032] In some possible embodiments, the planetary transmission member 6 includes a planetary gear 12, a planetary gear shaft 13, and a variable-speed cone 14. One end of the planetary gear shaft 13 is fixedly connected to the planetary gear 12 and is connected to one end of the planetary carrier 8 through a second bearing 15. The planetary gear 12 is meshed and connected with the sun cone gear 5. The variable-speed cone 14 is sleeved on the middle part of the planetary gear shaft 13. The other end of the planetary gear shaft 13 is connected to the other end of the planetary carrier 8 through a third bearing 16. The outer surface of the variable-speed cone 14 abuts against the inner ring surface of the variable-speed ring 7.

[0033] Specifically, the stepless speed change mechanism consists of two-stage transmission systems that cooperate with each other to achieve the stepless speed change function. The first stage is a planetary cone gear transmission with a fixed transmission ratio. By using the sun cone gear 5 key-connected to the input shaft 4 as the driving gear and the planetary gear 12 in the planetary transmission member 6 as the driven gear, the cone gear transmission is realized. The second stage is a friction drive, that is, the outer surface of the variable-speed cone 14 in the planetary transmission member 6 is used as the active friction surface, and the inner ring surface of the variable-speed ring 7 is used as the passive friction surface to realize the continuous change of the transmission ratio. Since the variable-speed ring 7 has only the freedom of axial movement, under the reaction force of the extrusion between the planetary gear 12 in the planetary transmission member 6 and the inner ring surface of the variable-speed ring 7, the planetary gear 12 rotates around the axis of the input shaft 4 along the inner ring surface of the variable-speed ring 7 while rotating on its own axis, driving the planetary carrier 8 and the output shaft 19 in the planetary carrier 8 to rotate, realizing the transmission of power.

[0034] In some possible embodiments, the planetary carrier 8 includes a sealing cover 17, a support frame 18, and an output shaft 19. The sealing cover 17 is fixedly connected to one end of the support frame 18 to form a sealed space. The sun cone gear 5 and the three planetary gears 12 are all located in the sealed space. The rear end of the input shaft 4 passes through the sealing cover 17 and is key-connected to the sun cone gear 5. The two ends of the support frame 18 are respectively connected to the two ends of the three planetary gear shafts 13 correspondingly. The middle part of the support frame 18 is distributed in the same direction as the axis of the input shaft 4 and is located at the center of the three planetary gear shafts 13. The other end of the support frame 18 is connected with an output shaft 19. The output shaft 19 is connected to the box body 1 through a fourth bearing 20.

[0035] Specifically, as Figures 6-7 shown, the planetary carrier 8 includes a sealing cover 17, a support frame 18, and an output shaft 19. Through the setting of the sealing cover 17, the sun cone gear 5 and the three planetary gears 12 are sealed and protected to prevent dust or other impurities from interfering with the meshing movement of the gears. Through the setting of the support frame 18, the whole planetary transmission member 6 is supported and fixed. When the support frame 18 is driven to rotate by the revolution of the planetary transmission member 6, the output shaft 19 rotates correspondingly, transmitting the power backward.

[0036] In some possible embodiments, the support frame 18 includes a first support disk 21, a connecting rod 22, and a second support disk 23. The centers of the first support disk 21 and the second support disk 23 are respectively fixed to both ends of the connecting rod 22. The first support disk 21 includes three symmetrically distributed first connecting plates 24. One ends of the three planetary gear shafts 13 are respectively connected to the three first connecting plates 24 through second bearings 15. The second support disk 23 includes three symmetrically distributed second connecting plates 25. The other ends of the three planetary gear shafts 13 are respectively connected to the three second connecting plates 25 through third bearings 16.

[0037] Specifically, as Figures 6-7 shown, since the variable speed cone barrel 14 with an inclination is adopted in the planetary transmission member 6, the first support disk 21 and the second support disk 23 with different sizes and heights are provided in the support frame 18, and the two ends of the planetary gear shaft 13 are fixed through the first connecting plates 24 and the second connecting plates 25 provided in the first support disk 21 and the second support disk 23, so that the outer surface of the variable speed cone barrel 14 is in parallel abutment with the inner ring surface of the variable speed ring 7, realizing the function of transmission speed change through the friction between the two.

[0038] In some possible embodiments, the rear end of the input shaft 4 passes through the sealing cover 17 and is connected to the center of the first support disk 21 through a fifth bearing 26.

[0039] Specifically, the rear end of the input shaft 4 is connected to the first support disk 21 through a fifth bearing 26, improving the conduction stability of the input shaft 4.

[0040] In some possible embodiments, the layout plane of any one of the first connecting plates 24 is parallel to the layout plane of any one of the second connecting plates 25.

[0041] Specifically, the layout plane of any one of the first connecting plates 24 is parallel to the layout plane of any one of the second connecting plates 25, so that both ends of the planetary gear shaft 13 are perpendicularly fixed to the first connecting plates 24 and the second connecting plates 25, making the two ends of the planetary gear shaft 13 stably fixed.

[0042] In some possible embodiments, a spring pressing mechanism 27 is provided at the connection between the variable speed cone barrel 14 and the planetary gear shaft 13.

[0043] Specifically, as Figure 1As shown, a spring pressing mechanism 27 is provided at the connection between the variable-speed cone barrel 14 and the planetary gear shaft 13. The spring pressing mechanism 27 includes a spring. The spring is disposed around the periphery of the planetary gear shaft 13, and the spring is pre-compressed during the installation process so that it has an axial force that causes the outer surface of the variable-speed cone barrel 14 to slide to the right from the very beginning, ensuring that the outer surface of the variable-speed cone barrel 14 is always in contact with the inner ring surface of the variable-speed ring 7 during the subsequent friction process of power transmission. Thus, through the setting of the spring pressing mechanism 27, a pressing force is provided for the friction contact point between the variable-speed cone barrel 14 and the variable-speed ring 7. With a sufficiently large pressing force, it is ensured that the friction drive between the variable-speed cone barrel 14 and the variable-speed ring 7 does not slip, thereby ensuring the transmission efficiency and improving the stability of the friction drive between the variable-speed cone barrel 14 and the variable-speed ring 7.

[0044] In some possible embodiments, the variable-speed ring 7 is provided with a threaded hole and a through hole. The speed-adjusting screw rod 10 is threadedly connected to the variable-speed ring 7 through the threaded hole. The variable-speed ring 7 is sleeved on the guide rod 11 through the through hole, and both ends of the guide rod 11 are threadedly connected to the box body 1.

[0045] Specifically, through the setting of the speed-adjusting screw rod 10, the axial displacement of the variable-speed ring 7 is realized; through the setting of the guide rod 11, the freedom degree of circumferential rotation of the variable-speed ring 7 is restricted.

[0046] In some possible embodiments, one end of the speed-adjusting screw rod 10 is connected to the box body 1, and the other end of the speed-adjusting screw rod 10 is connected to a shift motor 28. The shift motor 28 is fixedly installed on the box body 1.

[0047] Specifically, through the setting of the shift motor 28, the rotation speed of the speed-adjusting screw rod 10 is adjusted, and further the axial displacement of the variable-speed ring 7 is adjusted.

[0048] In some possible embodiments, the first bearing 9, the second bearing 15, the third bearing 16, the fourth bearing 20, and the fifth bearing 26 are all tapered roller bearings.

[0049] Specifically, the stepless speed change mechanism is respectively matched with the planetary bracket 8 through the input shaft 4 and the planetary gear shaft 13, and sliding bearings are provided at the corresponding matching positions to reduce the frictional resistance, reduce the wear, and improve the transmission efficiency.

[0050] Theoretical explanation of the speed change principle of the stepless speed change mechanism: On the basis of the transmission achieving power transmission, the circumferential fixation of the speed change ring 7 (equivalent to the circumferential gear ring in a conventional planetary gear train) can only move axially. When moving axially, the friction contact point between the speed change ring 7 and the speed change cone 14 is at different positions on the outer surface generatrix of the speed change cone 14. At this time, the working radius of the speed change cone 14 changes, that is, the cross-sectional radius at the friction contact point between the speed change cone 14 and the speed change ring 7 changes (which can be regarded as the radius of the planetary gear in a conventional planetary gear train changing), and the rotational speed of the revolution of the speed change cone 14 (the rotational speed of the planetary carrier 8) is determined by the rotational speed of its own rotation and the working radius at the friction contact point with the speed change ring 7.

[0051] When the speed change ring 7 slides axially, the working radius of the speed change cone 14 is changed, thereby changing the rotational speed of the planetary carrier 8, and this rotational speed of revolution is the output rotational speed of this transmission. The sun bevel gear 5 is the driving part, and the planetary carrier 8 is the driven part. The transmission ratio formula when the inner ring circumference of the speed change ring 7 is fixed:

[0052]

[0053] n 1 is the rotational speed of the sun bevel gear, n 3 is the rotational speed of the planetary carrier, Z i is the number of teeth of the sun bevel gear, Z 2 is the number of teeth equivalent to the inner ring circumference of the speed change ring.

[0054] Transform the above formula:

[0055]

[0056] r 1 is the radius of the sun bevel gear, r 2 is the inner ring radius of the speed change ring, r 3 is the working radius of the speed change cone.

[0057] It can be seen from the above formula that when the radius of the sun bevel gear 5 is fixed, when the speed change ring 7 moves towards the end with a larger working radius of the speed change cone 14, the revolution of the speed change cone 14 speeds up and the transmission ratio becomes larger; conversely, the transmission ratio becomes smaller.

[0058] Finally, it should be noted that the above embodiments are only specific embodiments of the present invention, which are used to illustrate the technical solutions of the present invention, rather than to limit it. The protection scope of the present invention is not limited thereto. Although the present invention has been described in detail with reference to the foregoing embodiments, those of ordinary skill in the art should understand that any person skilled in the art within the technical scope disclosed by the present invention can still modify the technical solutions recorded in the foregoing embodiments or can easily think of changes, or make equivalent replacements for some of the technical features; and these modifications, changes or replacements do not make the essence of the corresponding technical solutions deviate from the scope of the technical solutions of the embodiments of the present invention. All should be covered within the protection scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the protection scope of the claims.

[0059] Although the embodiments of the present invention have been disclosed above, it is not limited to the applications listed in the specification and embodiments. It can be fully applied to various fields suitable for the present invention. For those familiar with the field, additional modifications can be easily made. Therefore, without departing from the general concept defined by the claims and the equivalent scope, the present invention is not limited to the specific details and the illustrated and described examples here.

Claims

1. A hybrid transmission based on planetary bevel gear, characterized in that: The hybrid transmission comprises a housing (1), a drive motor (2), a clutch (3) and a continuously variable transmission mechanism, wherein the drive motor (2) and the continuously variable transmission mechanism are both arranged inside the housing (1); The continuously variable transmission mechanism comprises an input shaft (4), a sun bevel gear (5), three planetary transmission members (6), a speed change ring (7) and a planetary support (8); the front end of the input shaft (4) is connected to the housing (1) via a first bearing (9) and is key-connected to the clutch (3); the middle of the input shaft (4) is connected to the drive motor (2), and the rear end of the input shaft (4) is key-connected to the sun bevel gear (5); one end of each of the three planetary transmission members (6) is meshedly connected to the sun bevel gear (5), and the three planetary transmission members (6) are symmetrically arranged along the axial direction of the input shaft (4). The speed change ring (7) is sleeved on the periphery of the three planetary transmission members (6) so that the outer surfaces of the three planetary transmission members (6) are parallel to the inner ring surface of the speed change ring (7); the speed change ring (7) comprises a speed regulating screw (10) and a guide rod (11) arranged perpendicularly to the speed change ring (7); the speed change ring (7) is threadedly connected to the speed regulating screw (10), and both ends of the speed regulating screw (10) and the guide rod (11) are connected to the housing (1); and the two ends of the planetary bracket (8) are respectively connected to the three planetary transmission members (6) and the housing (1).

2. The hybrid transmission according to claim 1, characterized in that: The planetary transmission member (6) comprises a planetary gear (12), a planetary shaft (13) and a speed change cone cylinder (14); one end of the planetary shaft (13) is fixedly connected to the planetary gear (12) and is connected to one end of the planetary bracket (8) via a second bearing (15); the planetary gear (12) is meshingly connected to the sun bevel gear (5); the speed change cone cylinder (14) is sleeved on the middle part of the planetary shaft (13); the other end of the planetary shaft (13) is connected to the other end of the planetary bracket (8) via a third bearing (16); the outer surface of the speed change cone cylinder (14) is in contact with the inner ring surface of the speed change ring (7).

3. The hybrid transmission according to claim 2, characterized in that: The planetary bracket (8) comprises a sealing cover (17), a support frame (18) and an output shaft (19); the sealing cover (17) is fixedly connected to one end of the support frame (18) to form a sealed space; the sun bevel gear (5) and the three planetary gears (12) are all located in the sealed space; the rear end of the input shaft (4) passes through the sealing cover (17) and is key-connected to the sun bevel gear (5); the two ends of the support frame (18) are respectively connected to the two ends of the three planetary gear shafts (13); the middle part of the support frame (18) is distributed in the same direction as the axial direction of the input shaft (4) and is located at the center of the three planetary gear shafts (13); the other end of the support frame (18) is connected to the output shaft (19); the output shaft (19) is connected to the housing (1) via a fourth bearing (20).

4. The hybrid transmission according to claim 3, characterized in that: The support frame (18) comprises a first support plate (21), a connecting rod (22) and a second support plate (23), wherein the centers of the first support plate (21) and the second support plate (23) are respectively fixed to two ends of the connecting rod (22); the first support plate (21) comprises three symmetrically distributed first connecting plates (24), and one end of the three planetary gear shafts (13) is respectively connected to the three first connecting plates (24) via the second bearing (15); the second support plate (23) comprises three symmetrically distributed second connecting plates (25), and the other ends of the three planetary gear shafts (13) are respectively connected to the three second connecting plates (25) via the third bearing (16).

5. The hybrid transmission according to claim 4, characterized in that: The rear end of the input shaft (4) passes through the sealing cover (17) and is connected to the center of the first support plate (21) via a fifth bearing (26).

6. The hybrid transmission according to claim 5, characterized in that: The layout plane of any one of the first connecting plates (24) is parallel to the layout plane of any one of the second connecting plates (25).

7. The hybrid transmission according to claim 6, characterized in that: A spring pressing mechanism (27) is provided at the connection between the speed change cone (14) and the planetary gear shaft (13).

8. The hybrid transmission according to claim 7, characterized in that: The speed change ring (7) is provided with a threaded hole and a through hole, the speed regulating screw rod (10) is threadedly connected to the speed change ring (7) through the threaded hole, the speed change ring (7) is sleeved on the guide rod (11) through the through hole, and both ends of the guide rod (11) are threadedly connected to the box body (1).

9. The hybrid transmission according to claim 8, characterized in that: One end of the speed regulating screw rod (10) is connected to the housing (1), and the other end of the speed regulating screw rod (10) is connected to a gear shifting motor (28), and the gear shifting motor (28) is fixedly mounted on the housing (1).

10. The hybrid transmission according to claim 9, characterized in that: The first bearing (9), the second bearing (15), the third bearing (16), the fourth bearing (20) and the fifth bearing (26) are all tapered roller bearings.

Images