Single-sided input and output four-planetary-row continuously variable transmission mechanism and its speed change method

Abstract

The present invention discloses a four-planetary-row continuously variable transmission mechanism with single-sided input and output and its speed change method, belonging to the technical field of continuously variable transmissions. It includes a first planetary row, a second planetary row, a third planetary row and a fourth planetary row. The first ring gear on the first planetary row is connected to the second sun gear on the second planetary row through a first connecting shaft. The second ring gear on the second planetary row is connected to the third planet carrier on the third planetary row. The third planet carrier on the third planetary row is connected to the fourth sun gear on the fourth planetary row through a second connecting shaft. An output component is connected to the fourth planet carrier on the fourth planetary row. For the four-planetary-row continuously variable transmission mechanism with single-sided input and output of the present invention, the connection ends of the first driving member, the second driving member and the output component are all arranged at one end of the continuously variable transmission mechanism, so that the input and output of power are both at one end of the continuously variable transmission mechanism, thereby making the layout and space utilization rate of the entire power equipment more reasonable.

Description

Technical Field

[0001] The present invention relates to the technical field of continuously variable transmissions, and particularly relates to a four-planetary-row continuously variable transmission mechanism with single-sided input and output and a speed change method thereof. Background Art

[0002] With the increasing social requirements for environmental protection, electric vehicle technology has become the mainstream research direction of major automobile manufacturers. At present, most electric vehicles use a reducer with a fixed speed ratio. Although a reducer with a large speed ratio can be selected to meet the power requirements during vehicle starting and climbing, the large speed ratio limits the vehicle's maximum speed. This is also the reason why the maximum speed of electric vehicles in the market is generally lower than that of fuel vehicles. To balance the vehicle's maximum speed and climbing ability, many automobile manufacturers have started to install AMT transmissions on electric vehicles. However, the AMT transmission is a stepped transmission in principle and inherently has problems such as shift shock and power interruption; the transmission ratio range of the AMT transmission is restricted by the gear settings. When applied to heavy vehicles, to expand the transmission ratio range, a very large number of gears need to be set, the shift process is slow, and the operation is complex, resulting in many large truck drivers being reluctant to step on the brakes; the shift process of the AMT transmission depends on a complex control strategy, and it is difficult to grasp the accurate shift timing, resulting in high energy consumption and low efficiency; the structure of the AMT transmission is complex, the manufacturing cost is high, and the maintenance is difficult. Summary of the Invention

[0003] The purpose of the present invention is to solve the above problems and design a four-planetary-row continuously variable transmission mechanism with single-sided input and output and a speed change method thereof.

[0004] To achieve the above object, the technical solution of the present invention is a four - planetary - row continuously variable transmission mechanism with single - side input and output, including a first planetary row, a second planetary row, a third planetary row and a fourth planetary row. The first ring gear on the first planetary row is connected to the second sun gear on the second planetary row through a first connecting shaft. The second ring gear on the second planetary row is connected to the third planet carrier on the third planetary row. The third planet carrier on the third planetary row is connected to the fourth sun gear on the fourth planetary row through a second connecting shaft. An output component is connected to the fourth planet carrier on the fourth planetary row. The first planet carrier on the first planetary row, the second planet carrier on the second planetary row, the third ring gear on the third planetary row and the fourth ring gear on the fourth planetary row are all connected to a same - speed connecting body. A one - way stopper is arranged on the same - speed connecting body. The third sun gear on the third planetary row is connected to a second driving member through a second input shaft passing through the third planet carrier, the second connecting shaft, the fourth sun gear, the fourth planet carrier and the output component. The first sun gear on the first planetary row is connected to a first driving member through a first input shaft passing through the first connecting shaft, the second sun gear, the third sun gear, the second input shaft and the second driving member.

[0005] As a further description of the present invention, the first connecting shaft, the second sun gear, the third sun gear, the third planet carrier, the second connecting shaft, the fourth sun gear, the fourth planet carrier, the output component and the second input shaft are all of a through - hollow structure.

[0006] As a further description of the present invention, the one - way stopper is used to limit the rotation directions of the first planet carrier, the second planet carrier, the third ring gear and the fourth ring gear.

[0007] The present invention also provides a speed - change method based on the four - planetary - row continuously variable transmission mechanism with single - side input and output. The first driving member and the first sun gear are connected through the first input shaft, so that the rotational speed of the first driving member is the same as that of the first sun gear. The second driving member and the third sun gear are connected through the second input shaft, so that the rotational speed of the second driving member is the same as that of the third sun gear. The first planet carrier, the second planet carrier, the third ring gear and the fourth ring gear are all connected to the same - speed connecting body, so that the rotational speeds of the first planet carrier, the second planet carrier, the third ring gear and the fourth ring gear are the same. The first ring gear and the second sun gear are connected through the first connecting shaft, so that the rotational speed of the first ring gear is the same as that of the second sun gear. The second ring gear is connected to the third planet carrier, and the third planet carrier is connected to the fourth sun gear through the second connecting shaft, so that the rotational speeds of the second ring gear, the third planet carrier and the fourth sun gear are the same. The fourth planet carrier is connected to the output component, so that the rotational speed of the fourth planet carrier is the same as that of the output component.

[0008] For further illustration of the present invention, it is set that: the rotational speeds of the first driving member and the first sun gear are N1, the rotational speeds of the second driving member and the third sun gear are N2, the rotational speeds of the first planet carrier, the second planet carrier, the third ring gear and the fourth ring gear are N3, the rotational speeds of the first ring gear and the second sun gear are N4, the rotational speeds of the second ring gear, the third planet carrier and the fourth sun gear are N5, and the rotational speeds of the fourth planet carrier and the output member are N6; when any two of the values of N1, N2, N3, N4, N5, and N6 are determined, the other four values can be calculated through the proportional relationship of the line segments in the vector diagram. By adjusting and controlling the rotational speed N1 of the first driving member and the rotational speed N2 of the second driving member, continuous stepless change of the rotational speed N6 of the output member can be achieved. Among them, when the rotational speed N3 of the first planet carrier, the second planet carrier, the third ring gear and the fourth ring gear is 0, the ratio of the rotational speed N1 of the first driving member to the rotational speed N2 of the second driving member is set as P; by adjusting and controlling the rotational speed N1 of the first driving member and the rotational speed N2 of the second driving member, the output states of the output member include state A, state B, state C, state D, and state E.

[0009] For further illustration of the present invention, in state A, the rotational speed N3 of the first planet carrier, the second planet carrier, the third ring gear and the fourth ring gear is 0, the ratio of the rotational speed N1 of the first driving member to the rotational speed N2 of the second driving member is P, and the rotation directions are both positive, so that the rotation direction of the rotational speed N6 of the output member is positive. At this time, the transmission ratio is in the maximum state.

[0010] For further illustration of the present invention, in state B, the rotational speed N3 of the first planet carrier, the second planet carrier, the third ring gear and the fourth ring gear is not 0, the rotation direction is positive, the ratio of the rotational speed N1 of the first driving member to the rotational speed N2 of the second driving member is less than P, and the rotation directions are both positive, so that the rotation direction of the rotational speed N6 of the output member is positive.

[0011] As a further description of the present invention, in the state C, the rotational speeds N3 of the first planet carrier, the second planet carrier, the third ring gear, and the fourth ring gear are not 0, and the rotation directions are reverse. The ratio of the rotational speed N1 of the first driving member and the rotational speed N2 of the second driving member is greater than P, and the rotation directions are both forward. At this time, the rotation direction of the rotational speed N6 of the output member is reverse. In order to avoid the situation where the rotation direction of the rotational speed N6 of the output member is reverse, a one-way stopper is provided on the same-speed connector connecting the first planet carrier, the second planet carrier, the third ring gear, and the fourth ring gear. The one-way stopper restricts the rotation direction of the rotational speed N3 of the first planet carrier, the second planet carrier, the third ring gear, and the fourth ring gear to be only forward and not reverse, so that the rotation direction of the rotational speed N6 of the output member is always forward.

[0012] As a further description of the present invention, in the state D, the ratio of the rotational speed N1 of the first driving member and the rotational speed N2 of the second driving member is 1, and the rotation directions are both forward, so that the rotational speed N6 of the output member is equal to the rotational speeds N1 of the first driving member and N2 of the second driving member in magnitude, and the rotation directions are both forward. At this time, the transmission ratio is 1.

[0013] As a further description of the present invention, in the state E, the ratio of the rotational speed N1 of the first driving member and the rotational speed N2 of the second driving member is less than 1, and the rotation directions are both forward, so that the rotational speed N6 of the output member is greater than the rotational speeds N1 of the first driving member and N2 of the second driving member, and the rotation direction is forward.

[0014] As a further description of the present invention, when the first driving member fails, the rotational speed of the second driving member is N2, and the rotation direction is forward. The rotational speeds N3 of the first planet carrier, the second planet carrier, the third ring gear, and the fourth ring gear have a reverse rotation tendency. At this time, the one-way stopper restricts its reverse rotation, so that the rotational speeds N3 of the first planet carrier, the second planet carrier, the third ring gear, and the fourth ring gear are 0, the rotational speed N6 of the output member rotates forward, and the power of the second driving member is output through the third planetary gear set and the fourth planetary gear set after decelerating and increasing torque.

[0015] As a further description of the present invention, when the second driving member fails, the rotational speed of the first driving member is N1, and the rotation direction is forward. The rotational speeds N3 of the first planet carrier, the second planet carrier, the third ring gear, and the fourth ring gear have a reverse rotation tendency. At this time, the one-way stopper restricts its reverse rotation, so that the rotational speeds N3 of the first planet carrier, the second planet carrier, the third ring gear, and the fourth ring gear are 0, the rotational speed N6 of the output member rotates forward, and the power of the first driving member is output through the first planetary gear set, the second planetary gear set, and the fourth planetary gear set after decelerating and increasing torque.

[0016] The single-sided input and output four-planetary row continuously variable transmission mechanism and its speed change method provided by the present invention adjust the rotational speeds of the first driving member and the second driving member, and change the transmission ratio between the input end and the output end through the cooperation between the first planetary row, the second planetary row, the third planetary row, the fourth planetary row and the one-way stopper, realizing stepless speed change at the output end. This speed change mechanism has the advantages of high transmission efficiency, large output torque, no power interruption, simple and reliable structure, low manufacturing cost, easy maintenance and simple and convenient speed regulation. In addition, the connection ends of the first driving member, the second driving member and the output member are all arranged at one end of the continuously variable transmission mechanism, so that the input and output of power are both at one end of the continuously variable transmission mechanism, and the first input shaft is connected to the first driving member through the second input shaft and the second driving member. Such a design can greatly improve the space utilization rate and make the layout and space utilization rate of the entire power equipment more reasonable. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] Figure 1 is a schematic diagram of the single-sided input and output four-planetary row continuously variable transmission mechanism provided by an embodiment of the present invention;

[0018] Figure 2 is a rotational speed vector diagram of the first planetary row, the second planetary row, the third planetary row and the fourth planetary row provided by an embodiment of the present invention;

[0019] Figure 3 is a rotational speed vector diagram of combining the first planetary row, the second planetary row, the third planetary row and the fourth planetary row provided by an embodiment of the present invention;

[0020] Figure 4 is a rotational speed vector diagram when the ratio of the rotational speed N1 of the first driving member to the rotational speed N2 of the second driving member is less than P provided by an embodiment of the present invention;

[0021] Figure 5 is a rotational speed vector diagram when the ratio of the rotational speed N1 of the first driving member to the rotational speed N2 of the second driving member is greater than P provided by an embodiment of the present invention;

[0022] Figure 6 is a rotational speed vector diagram when the ratio of the rotational speed N1 of the first driving member to the rotational speed N2 of the second driving member is equal to 1 provided by an embodiment of the present invention;

[0023] Figure 7 is a rotational speed vector diagram when the ratio of the rotational speed N1 of the first driving member to the rotational speed N2 of the second driving member is less than 1 and the rotation directions are both positive provided by an embodiment of the present invention;

[0024] Figure 8 is a rotational speed vector diagram when the rotational speed N1 of the first driving member remains unchanged and the rotational speed N2 of the second driving member is adjusted provided by an embodiment of the present invention;

[0025] Figure 9 It is a rotational speed vector diagram when the rotational speed N2 of the second driving part provided by the embodiment of the present invention remains unchanged and the rotational speed N1 of the first driving part is adjusted.

[0026] Figure 10 It is a rotational speed vector diagram when the rotational speed N2 of the second driving part turns to the positive direction when the first driving part fails in the embodiment of the present invention.

[0027] Figure 11 It is a rotational speed vector diagram when the rotational speed N1 of the first driving part turns to the positive direction when the second driving part fails in the embodiment of the present invention.

[0028] Figure 12 It is a rotational speed vector diagram when the ratio of the rotational speed N1 of the first driving part to the rotational speed N2 of the second driving part provided by the embodiment of the present invention is equal to P and the rotation directions are both reverse.

[0029] Reference signs:

[0030] 1 - First planetary gear set, 101 - First sun gear, 102 - First planet carrier, 103 - First ring gear, 2 - Second planetary gear set, 201 - Second sun gear, 202 - Second planet carrier, 203 - Second ring gear, 3 - Third planetary gear set, 301 - Third sun gear, 302 - Third planet carrier, 303 - Third ring gear, 4 - Fourth planetary gear set, 401 - Fourth sun gear, 402 - Fourth planet carrier, 403 - Fourth ring gear, 5 - First input shaft, 6 - Second input shaft, 7 - First connecting shaft, 8 - Second connecting shaft, 9 - Output component, 10 - One-way stopper. Detailed implementation manners

[0031] First of all, we need to explain the purpose of applying for the embodiment of the present invention. We aim to solve the problems of shift shock and power interruption existing in AMT transmissions inherently; the transmission ratio range of AMT transmissions is restricted by gear settings. When applied to heavy vehicles, in order to expand the transmission ratio range, a very large number of gears need to be set, resulting in a slow shift process and complex operation, which is the reason why many large truck drivers are reluctant to step on the brakes; the shift process of AMT transmissions depends on complex control strategies, and it is very difficult to grasp the accurate shift timing, resulting in problems of high energy consumption and low efficiency; the structure of AMT transmissions is complex, with high manufacturing costs and difficult maintenance. Therefore, a four-planetary gear continuously variable transmission mechanism with single-sided input and output is proposed to solve the existing problems.

[0032] Next, the embodiments of the present invention will be specifically described with reference to the accompanying drawings. First, the specific structure of the embodiments of the present invention will be introduced.

[0033] See Figure 1, the four - planetary - row continuously variable transmission mechanism with single - side input and output provided by the embodiments of the present invention includes a first planetary row 1, a second planetary row 2, a third planetary row 3, and a fourth planetary row 4. The first ring gear 103 on the first planetary row 1 is connected to the second sun gear 201 on the second planetary row 2 through a first connecting shaft 7. The second ring gear 203 on the second planetary row 2 is connected to the third planetary carrier 302 on the third planetary row 3. The third planetary carrier 302 on the third planetary row 3 is connected to the fourth sun gear 401 on the fourth planetary row 4 through a second connecting shaft 8. An output component 9 is connected to the fourth planetary carrier 402 on the fourth planetary row 4. The first planetary carrier 102 on the first planetary row 1, the second planetary carrier 202 on the second planetary row 2, the third ring gear 303 on the third planetary row 3, and the fourth ring gear 403 on the fourth planetary row 4 are all connected to the same - speed connecting body. A one - way stopper 10 is provided on the same - speed connecting body. The third sun gear 301 on the third planetary row 3 is connected to a second driving member through a second input shaft 6 passing through the third planetary carrier 302, the second connecting shaft 8, the fourth sun gear 401, the fourth planetary carrier 402, and the output component 9. The first sun gear 101 on the first planetary row 1 is connected to a first driving member through a first input shaft …

[0034] See Figure 1 , the first planetary row 1 includes a first sun gear 101, a first planetary carrier 102, and a first ring gear 103. The second planetary row 2 includes a second sun gear 201, a second planetary carrier 202, and a second ring gear 203. The third planetary row 3 includes a third sun gear 301, a third planetary carrier 302, and a third ring gear 303. The fourth planetary row 4 includes a fourth sun gear 401, a fourth planetary carrier 402, and a fourth ring gear 403. In practical applications, the first connecting shaft 7, the second sun gear 201, the third sun gear 301, the third planetary carrier 302, the second connecting shaft 8, the fourth sun gear 401, the fourth planetary carrier 402, the output component 9, and the second input shaft 6 are all designed with a through - hole and hollow structure. The one - way stopper 10 is used to limit the rotation direction of the first planetary carrier 102, the second planetary carrier 202, the third ring gear 303, and the fourth ring gear 403.

[0035] Next, we need to describe the speed - change method of the four - planetary - row continuously variable transmission mechanism based on single - side input and output in combination with the specific structure of the embodiments of the present invention.

[0036] According to the basic principle of planetary gears, if the speeds of any two of the three components, namely the sun gear, the ring gear, and the planetary carrier, are determined, the speed of the other component is also determined, and their speed relationship is in a corresponding proportional relationship according to the number of teeth of the sun gear and the number of teeth of the ring gear.

[0037] According to the basic principle of planetary gears, when the rotational speeds of any two of the three components, namely the sun gear, the ring gear, and the planet carrier, are the same, the rotational speed of the other component is also the same.

[0038] Therefore, the rotational speed of the first driving component is the same as that of the first sun gear 101, designated as N1; the rotational speed of the second driving component is the same as that of the third sun gear 301, designated as N2; the rotational speeds of the first planet carrier 102, the second planet carrier 202, the third ring gear 303, and the fourth ring gear 403 are the same, designated as N3; the rotational speeds of the first ring gear 103 and the second sun gear 201 are the same, designated as N4; the rotational speeds of the second ring gear 203, the third planet carrier 302, and the fourth sun gear 401 are the same, designated as N5; the rotational speed of the fourth planet carrier 402 is the same as that of the output component 9, designated as N6.

[0039] Based on the rotational speed vector calculation method of planetary gears, the rotational speed vector diagrams of the first planetary gear set 1, the second planetary gear set 2, the third planetary gear set 3, and the fourth planetary gear set 4 are obtained, as Figure 2 shown. Figure 2 The length of the line segment in the diagram represents the magnitude of the rotational speed, and the arrow direction represents the rotational speed direction. It is defined that the upward arrow is the positive rotation direction, and the downward arrow is the reverse rotation direction.

[0040] Combining the rotational speed vector diagrams of the first planetary gear set 1, the second planetary gear set 2, the third planetary gear set 3, and the fourth planetary gear set 4 together, the rotational speed vector diagram as shown in Figure 3 is obtained.

[0041] Refer to Figure 3 , when any two of the values of N1, N2, N3, N4, N5, and N6 are determined, the other four values can be calculated through the proportional relationship of the line segments in the vector diagram. That is, when the rotational speed N1 of the first driving component is determined and the rotational speed N2 of the second driving component is determined, the rotational speed N6 of the output component 9 is also uniquely determined. By adjusting and controlling the rotational speed N1 of the first driving component and the rotational speed N2 of the second driving component, the continuous stepless change of the rotational speed N6 of the output component 9 can be achieved.

[0042] Next, the speed change principle of the four-planetary-gear stepless speed change mechanism with single-sided input and output according to the embodiment of the present invention will be described in combination with specific working conditions.

[0043] 1. Starting condition

[0044] Refer to Figure 3, at the start, the first driving part and the second driving part are started to accelerate. In terms of steering, the rotational speeds N1 of the first driving part and N2 of the second driving part are both in the positive direction. In terms of rotational speed, the ratio of the rotational speed N1 of the first driving part to the rotational speed N2 of the second driving part is equal to P. The rotational speed N6 of the output part 9 is gradually accelerated, and the steering is in the positive direction. Under this condition, the powers of the first driving part and the second driving part are coupled together, output with deceleration and torque increase, so that the vehicle accelerates forward.

[0045] 2. Acceleration and deceleration condition

[0046] See Figure 4 , during acceleration and deceleration, in terms of steering, the rotational speeds N1 of the first driving part and N2 of the second driving part are both in the positive direction. In terms of rotational speed, the ratio of the rotational speed N1 of the first driving part to the rotational speed N2 of the second driving part is less than P. By controlling the magnitudes of the rotational speeds N1 of the first driving part and N2 of the second driving part and the speed increase and decrease rates, the rotational speed N6 of the output part 9 can be gradually increased or decreased, the steering is in the positive direction, and the vehicle accelerates or decelerates forward.

[0047] In addition, as Figure 8 shown, the speed regulation methods for acceleration and deceleration can also be to keep the rotational speed N1 of the first driving part unchanged and adjust the magnitude of the rotational speed N2 of the second driving part to adjust the magnitude of the rotational speed N6 of the output part 9; as Figure 9 shown, it can also keep the rotational speed N2 of the second driving part unchanged and adjust the magnitude of the rotational speed N1 of the first driving part to adjust the magnitude of the rotational speed N6 of the output part 9. Therefore, during the process of accelerating or decelerating the rotational speed N6 of the output part 9, the first driving part and the second driving part can, according to their respective high-efficiency working areas, the control system controls the acceleration, deceleration, and rotational speed maintenance of the first driving part and the second driving part according to the current working condition. In this way, both the first driving part and the second driving part can work in their respective high-efficiency working areas for a long time, thus achieving the energy-saving effect.

[0048] 3. Maximum vehicle speed condition

[0049] See Figure 6 , when controlling the magnitudes of the rotational speeds N1 of the first driving part and N2 of the second driving part to be equal, the steering is in the positive direction for both, and when they both reach the maximum rotational speed, the rotational speed N6 of the output part 9 is also equal to the rotational speeds N1 of the first driving part and N? of the second driving part. It can be set that the vehicle reaches the maximum vehicle speed in this state.

[0050] See Figure 7, if the vehicle needs to reach a higher speed when it has reached the above maximum speed state, the rotation speed N1 of the first driving member can be reduced, and the rotation speed of the second driving member is maintained at the maximum rotation speed unchanged, so that the rotation speed N6 of the output member 9 continues to increase. The maximum speed is determined by the magnitude of the rotation speed N6 of the output member 9, and the magnitude of the rotation speed N6 of the output member 9 can be set by the rotation speed N1 of the first driving member and the rotation speed N2 of the second driving member. Therefore, as long as a first driving member with a lower rotation speed is selected, a very high output rotation speed can be achieved, and the power requirement for the driving member used is further reduced.

[0051] For the above-mentioned starting condition and acceleration / deceleration conditions, it is necessary to consider how to avoid the occurrence of a dangerous condition.

[0052] Example: Refer to Figure 5 , when the rotation speed control of the first driving member and the second driving member is inaccurate or the control fails, a situation where the ratio of the magnitudes of the rotation speed N1 of the first driving member and the rotation speed N2 of the second driving member is greater than P occurs, and when the rotations of both the rotation speed N1 of the first driving member and the rotation speed N2 of the second driving member are in the forward direction, the rotation speed N6 of the output member 9 may turn in the reverse direction. At this time, the vehicle suddenly reverses, and serious accidents are extremely likely to occur. To prevent this situation from happening, a one-way stopper 10 is provided on the same-speed connecting body jointly connected by the first planet carrier 102, the second planet carrier 202, the third ring gear 303, and the fourth ring gear 403 to limit the rotation direction of the rotation speed N3 of the first planet carrier 102, the second planet carrier 202, the third ring gear 303, and the fourth ring gear 403 to be only in the forward direction and not in the reverse direction. In this way, it is ensured that the rotation direction of the rotation speed N6 of the output member 9 is always in the forward direction. Therefore, when this dangerous condition occurs, since the one-way stopper 10 restricts the rotation direction of the rotation speed N3 of the first planet carrier 102, the second planet carrier 202, the third ring gear 303, and the fourth ring gear 403 to be only in the forward direction and not in the reverse direction, the two driving members will drag each other at this time, and the ratio of the magnitudes of the rotation speed N1 of the first driving member and the rotation speed N2 of the second driving member is always equal to P, the rotation speed N3 of the first planet carrier 102, the second planet carrier 202, the third ring gear 303, and the fourth ring gear 403 is equal to 0, and the rotation direction of the rotation speed N6 of the output member 9 can only be in the forward direction. Therefore, the vehicle will not suddenly reverse.

[0053] 4. Reverse condition

[0054] Refer to Figure 12, when reversing, the first driving member and the second driving member are activated to accelerate. In terms of steering, the rotational speeds N1 of the first driving member and N2 of the second driving member are both reversed, and in terms of rotational speed, the ratio of the rotational speed N1 of the first driving member to the rotational speed N2 of the second driving member is equal to P. The rotational speed N6 of the output member 9 is gradually accelerated and the steering is reversed. In this condition, the power of the first driving member and the second driving member is coupled together, decelerated and torque-increased for output, so that the vehicle accelerates backward.

[0055] In addition to the above normal conditions and dangerous conditions, there are also some emergency conditions that need to be dealt with, and the embodiments of the present invention have all considered and solved them.

[0056] Example: Refer to Figure 10 , when the first driving member fails, the rotational speed of the second driving member is N2 and the steering is forward. The rotational speeds N3 of the first planet carrier 102, the second planet carrier 202, the third ring gear 303 and the fourth ring gear 403 have a reverse tendency. At this time, the one-way stopper 10 restricts its reverse rotation, so that the rotational speeds N3 of the first planet carrier 102, the second planet carrier 202, the third ring gear 303 and the fourth ring gear 403 are 0, the rotational speed N6 of the output member 9 rotates forward, and the power of the second driving member is decelerated and torque-increased through the third planetary gear set 3 and the fourth planetary gear set 4 for output, so that the vehicle can continue to accelerate or decelerate forward.

[0057] Refer to Figure 11 , when the second driving member fails, the rotational speed of the first driving member is N1 and the steering is forward. The rotational speeds N3 of the first planet carrier 102, the second planet carrier 202, the third ring gear 303 and the fourth ring gear 403 have a reverse tendency. At this time, the one-way stopper 10 restricts its reverse rotation, so that the rotational speeds N3 of the first planet carrier 102, the second planet carrier 202, the third ring gear 303 and the fourth ring gear 403 are 0, the rotational speed N6 of the output member 9 rotates forward, and the power of the first driving member is decelerated and torque-increased through the first planetary gear set 1, the second planetary gear set 2 and the fourth planetary gear set 4 for output, so that the vehicle can continue to accelerate or decelerate forward.

[0058] Thus, it can be seen that when one driving member fails, the other driving member can still drive the vehicle. Although the power performance decreases, the vehicle can be driven to the repair location or a safe location by relying on one driving member, which can greatly improve the reliability of the vehicle.

[0059] The single-sided input and output four planetary gear set continuously variable transmission mechanism and its variable speed method provided by the embodiments of the present invention have the following advantages:

[0060] 1. The single-sided input and output four-planetary row continuously variable transmission mechanism according to the embodiment of the present invention has no power interruption during the speed regulation process, and operates quietly and stably. When users use the vehicle, they will have a better driving experience, which can greatly meet the customer needs in terms of sense, laying a very good foundation for the promotion and use of this product.

[0061] 2. The single-sided input and output four-planetary row continuously variable transmission mechanism according to the embodiment of the present invention can achieve large torque at the output end from low speed to high speed. By outputting a large torque, the vehicle has the ability to accelerate quickly when starting, and the large torque can enable the vehicle to climb a steeper slope when climbing a hill. The large torque can also meet the vehicle use needs of more people, making the audience of this product larger.

[0062] 3. The single-sided input and output four-planetary row continuously variable transmission mechanism according to the embodiment of the present invention can achieve stepless and continuous change of the output speed. The input drive member can work in the high-efficiency range for a long time, improving the work efficiency, achieving a more energy-saving effect in terms of energy use, and making more contributions in energy conservation.

[0063] 4. The single-sided input and output four-planetary row continuously variable transmission mechanism according to the embodiment of the present invention has simple and convenient speed regulation. Only by controlling the speeds of the first drive member and the second drive member can stepless and continuous change of the output speed be achieved, thereby reducing the requirements of the vehicle for the control system, making the promotion and use range of this product wider, and ensuring the promotion and popularity of this product to a certain extent.

[0064] 5. The power of the first drive member and the second drive member in the embodiment of the present invention is coupled to drive the vehicle to travel. When one of the drive members fails, the other drive member can still continue to drive the vehicle, ensuring that when the vehicle owner uses the car, even if one drive member fails, the vehicle owner can still rely on the other drive member to drive the car and drive the car to the repair location in time, avoiding the occurrence of the need to call a tow truck, and better taking care of the vehicle use experience of the vehicle owner.

[0065] 6. Compared with the traditional driving method of a single drive member, using the product according to the embodiment of the present invention can not only use two drive members for driving, but also select drive members with smaller volume and lower speed for matching. The small-volume drive members are more conducive to the layout design of the drive members in the vehicle body, making it more convenient for the later aesthetic design of the vehicle body, and using smaller drive members can save costs.

[0066] 7. The single-sided input and output four planetary row continuously variable transmission mechanism of the embodiment of the present invention has a high transmission efficiency. Under the same working conditions, a motor with a lower power and a lower speed can be selected as the driving part. Compared with a high-power battery, a low-power battery can better prevent the occurrence of battery overheating, indirectly improving the safety of battery use through the embodiment of the present invention.

[0067] 8. The single-sided input and output four planetary row continuously variable transmission mechanism of the embodiment of the present invention adopts four planetary row transmissions, increasing the transmission ratio and further increasing the torque. It can be applied to heavy-duty vehicles such as trucks, muck trucks, and buses with a greater load, further expanding the scope of application of the embodiment of the present invention.

[0068] 9. The single-sided input and output four planetary row continuously variable transmission mechanism of the embodiment of the present invention sets the connection ends of the first driving part, the second driving part, and the output component at one end of the continuously variable transmission mechanism, enabling the input and output of power to be at one end of the continuously variable transmission mechanism. Moreover, the first input shaft passes through the second input shaft and the second driving part to be connected to the first driving part. Such a design can greatly improve the utilization rate of space, making the arrangement and space utilization rate of the entire power equipment more reasonable.

[0069] The above technical solutions only reflect the preferred technical solutions of the technical solutions of the present invention. Some possible changes made by those skilled in the art to some parts thereof all reflect the principles of the present invention and fall within the protection scope of the present invention.

Claims

1. A speed change method for a four-planetary-gear continuously variable transmission mechanism with single-sided input and output, characterized in that The single-sided input and output four-planetary row continuously variable transmission mechanism includes a first planetary row (1), a second planetary row (2), a third planetary row (3) and a fourth planetary row (4). The first ring gear (103) on the first planetary row (1) is connected to the second sun gear (201) on the second planetary row (2) through a first connecting shaft (7). The second ring gear (203) on the second planetary row (2) is connected to the third planetary carrier (302) on the third planetary row (3). The third planetary carrier (302) on the third planetary row (3) is connected to the fourth sun gear (401) on the fourth planetary row (4) through a second connecting shaft (8). An output component (9) is connected to the fourth planetary carrier (402) on the fourth planetary row (4). The first planetary carrier (102) on the first planetary row (1), the second planetary carrier (202) on the second planetary row (2), the third ring gear (303) on the third planetary row (3) and the fourth ring gear (403) on the fourth planetary row (4) are all connected to the same-speed connecting body. A one-way stopper (10) is arranged on the same-speed connecting body. The third sun gear (301) on the third planetary row (3) is connected to a second driving member through a second input shaft (6) passing through the third planetary carrier (302), the second connecting shaft (8), the fourth sun gear (401), the fourth planetary carrier (402) and the output component (9). The first sun gear (101) on the first planetary row (1) is connected to a first driving member through a first input shaft (5) passing through the first connecting shaft (7), the second sun gear (201), the third sun gear (301), the second input shaft (6) and the second driving member; The first connecting shaft (7), the second sun gear (201), the third sun gear (301), the third planetary carrier (302), the second connecting shaft (8), the fourth sun gear (401), the fourth planetary carrier (402), the output component (9) and the second input shaft (6) are all of a through-hollow structure; The one-way stopper (10) is used to limit the rotation direction of the first planetary carrier (102), the second planetary carrier (202), the third ring gear (303) and the fourth ring gear (403); The first driving member and the first sun gear (101) are connected by the first input shaft (5) so that the rotational speed of the first driving member is the same as that of the first sun gear (101); the second driving member and the third sun gear (301) are connected by the second input shaft (6) so that the rotational speed of the second driving member is the same as that of the third sun gear (301); the first planet carrier (102), the second planet carrier (202), the third ring gear (303) and the fourth ring gear (403) are all connected to the same-speed connecting body so that the rotational speeds of the first planet carrier (102), the second planet carrier (202), the third ring gear (303) and the fourth ring gear (403) are the same; the first ring gear (103) and the second sun gear (201) are connected by the first connecting shaft (7) so that the rotational speed of the first ring gear (103) is the same as that of the second sun gear (201); the second ring gear (203) is connected to the third planet carrier (302), and the third planet carrier (302) is connected to the fourth sun gear (401) by the second connecting shaft (8) so that the rotational speeds of the second ring gear (203), the third planet carrier (302) and the fourth sun gear (401) are the same; the fourth planet carrier (402) is connected to the output member (9) so that the rotational speed of the fourth planet carrier (402) is the same as that of the output member (9).

2. The speed change method of the four planetary row continuously variable transmission mechanism with single-sided input and output according to claim 1, characterized in that, It is set that: the rotational speeds of the first driving member and the first sun gear (101) are N1, the rotational speeds of the second driving member and the third sun gear (301) are N2, the rotational speeds of the first planet carrier (102), the second planet carrier (202), the third ring gear (303) and the fourth ring gear (403) are N3, the rotational speeds of the first ring gear (103) and the second sun gear (201) are N4, the rotational speeds of the second ring gear (203), the third planet carrier (302) and the fourth sun gear (401) are N5, and the rotational speeds of the fourth planet carrier (402) and the output member (9) are N6; when any two of the values of N1, N2, N3, N4, N5, and N6 are determined, the other four values can be calculated through the proportional relationship of the line segments in the vector diagram, and by adjusting and controlling the rotational speed N1 of the first driving member and the rotational speed N2 of the second driving member, the continuous stepless change of the rotational speed N6 of the output member (9) can be achieved. Among them, when the rotational speed N3 of the first planet carrier (102), the second planet carrier (202), the third ring gear (303) and the fourth ring gear (403) is 0, the ratio of the rotational speed N1 of the first driving member and the rotational speed N2 of the second driving member is set as P; by adjusting and controlling the rotational speed N1 of the first driving member and the rotational speed N2 of the second driving member, the output states of the output member (9) include state A, state B, state C, state D and state E.

3. The speed change method of the four planetary row continuously variable transmission mechanism with single-sided input and output according to claim 2, characterized in that, In the state A, the rotational speeds N3 of the first planet carrier (102), the second planet carrier (202), the third ring gear (303), and the fourth ring gear (403) are 0. The ratio of the rotational speed N1 of the first driving member to the rotational speed N2 of the second driving member is P, and the rotation directions are both positive, causing the rotation direction of the rotational speed N6 of the output member (9) to be positive. At this time, it is in the state of the maximum transmission ratio.

4. The speed change method of the four planetary row continuously variable transmission mechanism with single-sided input and output according to claim 2, characterized in that In the state B, the rotational speeds N3 of the first planet carrier (102), the second planet carrier (202), the third ring gear (303), and the fourth ring gear (403) are not 0, and the rotation direction is positive. The ratio of the rotational speed N1 of the first driving member to the rotational speed N2 of the second driving member is less than P, and the rotation directions are both positive, causing the rotation direction of the rotational speed N6 of the output member (9) to be positive.

5. The speed change method of the four planetary gear row continuously variable transmission mechanism with single-sided input and output according to claim 2, characterized in that, In the state C, the rotational speeds N3 of the first planet carrier (102), the second planet carrier (202), the third ring gear (303), and the fourth ring gear (403) are not 0, and the rotation direction is negative. The ratio of the rotational speed N1 of the first driving member to the rotational speed N2 of the second driving member is greater than P, and the rotation directions are both positive. At this time, the rotation direction of the rotational speed N6 of the output member (9) is negative. To avoid the situation where the rotation direction of the rotational speed N6 of the output member (9) is negative, a one-way stopper (10) is provided on the same-speed connecting body connected to the first planet carrier (102), the second planet carrier (202), the third ring gear (303), and the fourth ring gear (403). The one-way stopper (10) restricts the rotation direction of the rotational speed N3 of the first planet carrier (102), the second planet carrier (202), the third ring gear (303), and the fourth ring gear (403) to only be positive and not negative, causing the rotation direction of the rotational speed N6 of the output member (9) to always be positive.

6. The speed change method of the four planetary row continuously variable transmission mechanism with single-sided input and output according to claim 2, characterized in that, In the state D, the ratio of the rotational speed N1 of the first driving member to the rotational speed N2 of the second driving member is 1, and the rotation directions are both positive, causing the rotational speed N6 of the output member (9) to be equal to the rotational speeds N1 of the first driving member and N2 of the second driving member, and the rotation directions are both positive. At this time, the transmission ratio is 1.

7. The speed change method of the four planetary row continuously variable transmission mechanism with single-sided input and output according to claim 2, characterized in that, In the state E, the ratio of the rotational speed N1 of the first driving member to the rotational speed N2 of the second driving member is less than 1, and the rotation directions are both positive, causing the rotational speed N6 of the output member (9) to be greater than the rotational speeds N1 of the first driving member and N2 of the second driving member, and the rotation direction is positive.

8. The speed change method of the four planetary row continuously variable transmission mechanism with single-sided input and output according to claim 2, characterized in that, When the first driving member fails, the rotational speed of the second driving member is N2 and the rotation direction is forward. The rotational speeds N3 of the first planet carrier (102), the second planet carrier (202), the third ring gear (303) and the fourth ring gear (403) have a reverse tendency. At this time, the one-way stopper (10) restricts their reverse rotation, so that the rotational speeds N3 of the first planet carrier (102), the second planet carrier (202), the third ring gear (303) and the fourth ring gear (403) are 0. The rotational speed N6 of the output member (9) rotates forward, and the power of the second driving member is output after being decelerated and torque-increased by the third planetary gear set (3) and the fourth planetary gear set (4).

9. The speed change method of the four planetary row continuously variable transmission mechanism with single-sided input and output according to claim 2, characterized in that, When the second driving member fails, the rotational speed of the first driving member is N1 and the rotation direction is forward. The rotational speeds N3 of the first planet carrier (102), the second planet carrier (202), the third ring gear (303) and the fourth ring gear (403) have a reverse tendency. At this time, the one-way stopper (10) restricts their reverse rotation, so that the rotational speeds N3 of the first planet carrier (102), the second planet carrier (202), the third ring gear (303) and the fourth ring gear (403) are 0. The rotational speed N6 of the output member (9) rotates forward, and the power of the first driving member is output after being decelerated and torque-increased by the first planetary gear set (1), the second planetary gear set (2) and the fourth planetary gear set (4).

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