A dual-drive four-planetary-gear continuously variable transmission mechanism and its speed change method

Abstract

The present invention discloses a dual-drive four-planetary-row continuously variable transmission mechanism, 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 planetary carrier on the third planetary row. The third planetary 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 planetary carrier on the fourth planetary row. A one-way stopper is provided on one side of the same-speed connecting body. The present invention also discloses a speed change method for the dual-drive four-planetary-row continuously variable transmission mechanism. The connection ends of the input end and the output end of the dual-drive four-planetary-row continuously variable transmission mechanism of the present invention are respectively arranged at both ends thereof, avoiding the situation that the input end and the output end will affect each other during operation, thereby reducing the overall failure rate.

Description

Technical Field

[0001] The present invention relates to the technical field of continuously variable transmissions, and particularly relates to a dual-drive four-planetary-row continuously variable transmission mechanism 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 fixed-ratio reducer. Although a large-ratio reducer can be selected to meet the power requirements during vehicle starting and climbing, the large ratio limits the vehicle's ability to reach a high maximum speed, which is also the reason why the maximum speed of electric vehicles in the market is generally lower than that of fuel vehicles. In order to balance the maximum speed and climbing ability of the vehicle, many automobile manufacturers have begun to install AMT transmissions on electric vehicles. However, the AMT transmission belongs to 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, in order to expand the transmission ratio range, a very large number of gears need to be set, the shifting process is slow, and the operation is complex, resulting in many large truck drivers being reluctant to step on the brakes; the shifting process of the AMT transmission relies on complex control strategies, it is difficult to grasp the accurate shifting timing, and there are problems of 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 dual-drive four-planetary-row continuously variable transmission mechanism and a speed change method thereof.

[0004] The technical solution of the present invention for achieving the above purpose is a dual-drive four-planetary-row continuously variable transmission mechanism, 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 planetary carrier on the third planetary row. The third planetary 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 planetary carrier on the fourth planetary row. The first planetary carrier on the first planetary row, the second planetary 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-rotation-speed connecting body. A one-way stopper is provided on the same-rotation-speed connecting body. The first sun gear on the first planetary row is connected to a first driving member through a first input shaft. The third sun gear on the third planetary row is connected to a second driving member through a second input shaft passing through the second sun gear, the first connecting shaft, the first sun gear, the first input shaft, and the first driving member.

[0005] As a further description of the present invention, the second sun gear, the first connecting shaft, the first sun gear, the first input shaft and the first driving member 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 a dual-drive four-planet row continuously variable transmission mechanism. 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 member, so that the rotational speed of the fourth planet carrier is the same as that of the output member.

[0008] As a further description 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 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 include state A, state B, state C, state D and state E.

[0009] As a further description of the present invention, in the state A, 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 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] As a further description of the present invention, in the state B, 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 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 direction is reverse. 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 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-rotational-speed connecting body connected to 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 only be positive and not reverse, so that the rotation direction of the rotational speed N6 of the output member is always positive.

[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 to the rotational speed N2 of the second driving member is 1, and the rotation directions are both positive, so that the rotational speed N6 of the output member is equal in magnitude 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.

[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 to the rotational speed N2 of the second driving member is less than 1, and the rotation directions are both positive, 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 positive.

[0014] As a further illustration 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 tendency. At this time, the one-way stopper restricts their reverse rotation, making the rotational speeds N3 of the first planet carrier, the second planet carrier, the third ring gear, and the fourth ring gear 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 illustration 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 tendency. At this time, the one-way stopper restricts their reverse rotation, making the rotational speeds N3 of the first planet carrier, the second planet carrier, the third ring gear, and the fourth ring gear 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 dual-drive four-planetary-gear 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 through the cooperation between the first planetary gear set, the second planetary gear set, the third planetary gear set, the fourth planetary gear set, and the one-way stopper, change the transmission ratio between the input end and the output end to achieve 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 input end and the output end of the dual-drive four-planetary-gear continuously variable transmission mechanism of the present invention are respectively arranged at both ends, avoiding the situation where the input end and the output end affect each other during operation, thereby reducing the overall failure rate. Brief Description of the Drawings

[0017] Figure 1 is a schematic diagram of the dual-drive four-planetary-gear 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 gear set, the second planetary gear set, the third planetary gear set, and the fourth planetary gear set provided by an embodiment of the present invention;

[0019] Figure 3 is a combined rotational speed vector diagram of the first planetary gear set, the second planetary gear set, the third planetary gear set, and the fourth planetary gear set 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 provided by an embodiment of the present invention is less than P;

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

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

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

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

[0025] Figure 9 The rotational speed vector diagram when the rotational speed N2 of the second driving member is kept unchanged and the rotational speed N1 of the first driving member is adjusted is provided in an embodiment of the present invention;

[0026] Figure 10 A speed vector diagram of the second driving member when the speed N2 turns to the forward direction when the first driving member fails, provided by an embodiment of the present invention;

[0027] Figure 11 A speed vector diagram of the first driving member when the speed N1 turns to the forward direction when the second driving member fails, provided by an embodiment of the present invention;

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

[0029] Reference numerals:

[0030] 1-First planetary row, 101-First sun gear, 102-First planetary carrier, 103-First ring gear, 2-Second planetary row, 201-Second sun gear, 202-Second planetary carrier, 203-Second ring gear, 3-Third planetary row, 301-Third sun gear, 302-Third planetary carrier, 303-Third ring gear, 4-Fourth planetary row, 401-Fourth sun gear, 402-Fourth planetary 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 DESCRIPTION

[0031] First, we need to explain the purpose of filing this embodiment of the invention. We aim to solve the problems inherent in AMT transmissions, such as shift jerks and power interruptions. The transmission ratio range of AMT transmissions is restricted by the gear settings. When applied to heavy-duty vehicles, to expand the transmission ratio range, a large number of gears need to be set, resulting in a slow shifting process and complex operation, which is why many truck drivers are reluctant to step on the brakes. The shifting process of AMT transmissions relies on complex control strategies, making it difficult to grasp the accurate shifting timing, leading to high energy consumption and low efficiency. AMT transmissions also have problems such as complex structure, high manufacturing cost, and difficult maintenance. Therefore, a dual-drive four-planetary-row continuously variable transmission mechanism is proposed to solve the existing problems.

[0032] Next, we will specifically describe this embodiment of the invention in conjunction with the accompanying drawings. First, let's introduce the specific structure of this embodiment of the invention.

[0033] See Figure 1 , the dual-drive four-planetary-row continuously variable transmission mechanism provided by this embodiment of the 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 first sun gear 101 on the first planetary row 1 is connected to a first driving member through a first input shaft 5. The third sun gear 301 on the third planetary row 3 is connected to a second driving member through a second input shaft 6 that passes through the second sun gear 201, the first connecting shaft 7, the first sun gear 101, the first input shaft 5, and the first driving member.

[0034] See Figure 1, the first planetary gear set 1 includes a first sun gear 101, first planet gears, and a first ring gear 103; the second planetary gear set 2 includes a second sun gear 201, a second planet carrier 202, and a second ring gear 203; the third planetary gear set 3 includes a third sun gear 301, a third planet carrier 302, and a third ring gear 303; the fourth planetary gear set 4 includes a fourth sun gear 401, a fourth planet carrier 402, and a fourth ring gear 403. In practical applications, the second sun gear 201, the first connecting shaft 7, the first ring gear 103, the first sun gear 101, the first input shaft 5, and the first driving member are all designed with a through-hole hollow structure. The one-way stopper 10 is used to limit the rotation directions of the first planet carrier 102, the second planet carrier 202, the third ring gear 303, and the fourth ring gear 403.

[0035] Next, we need to describe the speed change method based on the dual-drive four-planetary-gear continuously variable transmission mechanism 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 planet 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, if the speeds of any two of the three components, namely the sun gear, the ring gear, and the planet carrier, are the same, the speed of the other component is also the same.

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

[0039] According to the speed vector calculation method of planetary gears, the 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 In the figure, the length of the line segment represents the magnitude of the speed, and the arrow direction represents the speed direction. It is defined that the arrow pointing upward is the positive rotation direction, and the arrow pointing downward is the negative rotation direction.

[0040] The 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 combined to obtain the speed vector diagram as Figure 3 shown.

[0041] SeeFigure 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 member is determined and the rotational speed N2 of the second driving member is determined, the rotational speed N6 of the output member 9 is also uniquely determined. By adjusting and controlling the rotational speed N1 of the first driving member and the rotational speed N2 of the second driving member, a continuously variable stepless change in the rotational speed N6 of the output member 9 can be achieved.

[0042] Next, the speed change principle of the dual-drive four-planetary row continuously variable transmission mechanism 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 , when starting, start the first driving member and the second driving member to accelerate. In terms of steering, control the rotational speeds N1 of the first driving member and N2 of the second driving member to be both positive. In terms of rotational speed, control the ratio of the rotational speed N1 of the first driving member to the rotational speed N2 of the second driving member to be equal to P. Gradually accelerate the rotational speed N6 of the output member 9, and the steering is positive. In this condition, the powers of the first driving member and the second driving member are coupled together, and the output is decelerated and torque-increased to make the vehicle accelerate forward.

[0045] 2. Acceleration and deceleration conditions

[0046] Refer to Figure 4 , when accelerating or decelerating, in terms of steering, control the rotational speeds N1 of the first driving member and N2 of the second driving member to be both positive. In terms of rotational speed, control the ratio of the rotational speed N1 of the first driving member to the rotational speed N2 of the second driving member to be less than P. By controlling the magnitudes of the rotational speeds N1 of the first driving member and N2 of the second driving member and the speed increase and decrease rates, it is possible to gradually increase or decrease the rotational speed N6 of the output member 9, and the steering is positive, so that 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 member unchanged and adjust the magnitude of the rotational speed N2 of the second driving member to adjust the magnitude of the rotational speed N6 of the output member 9; as Figure 9 shown, it is also possible to keep the rotational speed N2 of the second driving member unchanged and adjust the magnitude of the rotational speed N1 of the first driving member to adjust the magnitude of the rotational speed N6 of the output member 9. Therefore, during the process of accelerating or decelerating the rotational speed N6 of the output member 9, the first driving member and the second driving member can, according to their respective high-efficiency working areas, the control system controls the acceleration, deceleration, and speed maintenance of the first driving member and the second driving member according to the current working conditions. In this way, both the first driving member and the second driving member can work in their respective high-efficiency working areas for a long time, thereby achieving the effect of energy saving.

[0048] 3. Maximum vehicle speed condition

[0049] See Figure 6 , when the rotational speeds N1 of the first driving member and N2 of the second driving member are controlled to be equal in magnitude, both with a forward direction of rotation and both reaching the maximum rotational speed, the rotational speed N6 of the output member 9 is also equal to the rotational speed N1 of the first driving member and the rotational speed N2 of the second driving member. 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 in the above maximum vehicle speed state, the rotational speed N1 of the first driving member can be reduced, while maintaining the rotational speed of the second driving member at the maximum rotational speed unchanged, so that the rotational speed N6 of the output member 9 continues to increase. The maximum vehicle speed is determined by the magnitude of the rotational speed N6 of the output member 9, and the magnitude of the rotational speed N6 of the output member 9 can be set by the rotational speed N1 of the first driving member and the rotational speed N2 of the second driving member. Therefore, as long as a first driving member with a lower rotational speed is selected, a very high output rotational speed can be achieved, further reducing the power requirement for the driving member used.

[0051] Regarding the above-mentioned starting condition and acceleration / deceleration conditions, the occurrence of a dangerous condition needs to be considered for how to avoid it.

[0052] Example: See Figure 5 , when the rotational speed control of the first driving member and the second driving member is inaccurate or the control fails, and the ratio of the magnitude 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 rotational directions of the rotational speed N1 of the first driving member and the rotational speed N2 of the second driving member are both forward, the rotational speed N6 of the output member 9 may turn in the reverse direction. At this time, the vehicle suddenly reverses, which is extremely likely to cause serious accidents. To prevent this situation from occurring, a one-way stopper 10 is provided on the co-rotating 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 rotational 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 forward and not reverse. In this way, it is ensured that the rotational direction of the rotational speed N6 of the output member 9 is always forward. Therefore, when this dangerous condition occurs, since the one-way stopper 10 restricts the rotational 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 forward and not reverse, at this time, the two driving members will drag each other, the ratio of the magnitude of the rotational speed N1 of the first driving member to the rotational speed N2 of the second driving member is always equal to P, 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 equal to 0, and the rotational direction of the rotational speed N6 of the output member 9 can only be forward. Therefore, the vehicle will not suddenly reverse.

[0053] 4. Reverse driving condition

[0054] See Figure 12 , when reversing, start the first driving part and the second driving part to accelerate. In terms of steering, control the rotational speeds N1 of the first driving part and N2 of the second driving part to be both in the reverse direction. In terms of rotational speed, control the ratio of the rotational speed N1 of the first driving part to the rotational speed N2 of the second driving part to be equal to P. Gradually accelerate the rotational speed N6 of the output component 9, and the steering is in the reverse direction. In this condition, the powers of the first driving part and the second driving part are coupled together, and the speed is reduced and the torque is 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 taken them into consideration and solved them.

[0056] Example: See Figure 10 , when the first driving part fails, the rotational speed of the second driving part is N2, and the steering is in the forward direction. 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 rotation 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 component 9 rotates in the forward direction, and the power of the second driving part is output through the third planetary gear set 3 and the fourth planetary gear set 4 with speed reduction and torque increase, so that the vehicle can continue to accelerate or decelerate forward.

[0057] See Figure 11 , when the second driving part fails, the rotational speed of the first driving part is N1, and the steering is in the forward direction. 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 rotation 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 component 9 rotates in the forward direction, and the power of the first driving part is output through the first planetary gear set 1, the second planetary gear set 2, and the fourth planetary gear set 4 with speed reduction and torque increase, so that the vehicle can continue to accelerate or decelerate forward.

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

[0059] The dual-drive four-planetary-gearset continuously variable transmission mechanism and its variable speed method provided by the embodiments of the present invention have the following advantages:

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

[0061] 2. The dual-drive four-planetary-gear continuously variable transmission mechanism according to the embodiments 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 usage needs of more people, making the target audience of this product larger.

[0062] 3. The dual-drive four-planetary-gear continuously variable transmission mechanism according to the embodiments 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 to energy conservation.

[0063] 4. The dual-drive four-planetary-gear continuously variable transmission mechanism according to the embodiments 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 embodiments 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 owner's driving experience.

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

[0066] 7. The dual-drive four-planetary-gear continuously variable transmission mechanism according to the embodiments of the present invention has a high transmission efficiency. Under the same working conditions, motors with lower power and lower speed can be selected as drive members. Compared with high-power batteries, small-power batteries can better prevent the occurrence of battery overheating, indirectly improving the use safety of the battery through the embodiments of the present invention.

[0067] 8. The dual-drive four-planetary-row continuously variable transmission mechanism of the embodiment of the present invention adopts a four-planetary-row transmission, which increases the transmission ratio and further increases 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 connection ends of the input end and the output end of the dual-drive four-planetary-row continuously variable transmission mechanism of the embodiment of the present invention are respectively arranged at both ends thereof, avoiding the situation that the input end and the output end affect each other during operation, and thus reducing the overall failure rate.

[0069] The above technical solutions only reflect the preferred technical solutions of the technical solutions of the present invention. Some changes that those skilled in the art may make 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 double-drive four-planetary row continuously variable transmission mechanism, characterized in that, The double-drive 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). A first ring gear (103) on the first planetary row (1) is connected to a second sun gear (201) on the second planetary row (2) through a first connecting shaft (7). A second ring gear (203) on the second planetary row (2) is connected to a third planetary carrier (302) on the third planetary row (3). The third planetary carrier (302) on the third planetary row (3) is connected to a fourth sun gear (401) on the fourth planetary row (4) through a second connecting shaft (8). An output component (9) is connected to a fourth planetary carrier (402) on the fourth planetary row (4). A first planetary carrier (102) on the first planetary row (1), a second planetary carrier (202) on the second planetary row (2), a third ring gear (303) on the third planetary row (3), and a fourth ring gear (403) on the fourth planetary row (4) are all connected to a same-rotation-speed connecting body. A one-way stopper (10) is arranged on the same-rotation-speed connecting body. A first sun gear (101) on the first planetary row (1) is connected to a first driving member through a first input shaft (5). A third sun gear (301) on the third planetary row (3) is connected to a second driving member through a second input shaft (6) that passes through the second sun gear (201), the first connecting shaft (7), the first sun gear (101), the first input shaft (5), and the first driving member; The second sun gear (201), the first connecting shaft (7), the first sun gear (101), the first input shaft (S), and the first driving member are all of a through-hollow structure; The one-way stopper (10) is used to limit the rotation directions 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-rotational-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 dual-drive four planetary gear trains continuously variable transmission mechanism 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. 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 (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 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 (9) include state A, state B, state C, state D and state E.

3. The speed change method of the dual-drive four planetary gear train continuously variable transmission mechanism 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 and the rotational speed N2 of the second driving member is P, and the directions of rotation are both positive, so that the direction of rotation of the rotational speed N6 of the output member (9) is positive. At this time, the transmission ratio is in the maximum state.

4. The speed change method of the dual-drive four-planetary-gear continuously variable transmission mechanism 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, the direction of rotation is positive, 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 P, and the directions of rotation are both positive, so that the direction of rotation of the rotational speed N6 of the output member (9) is positive.

5. The speed change method of the dual-drive four planetary gear row continuously variable transmission mechanism 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, the direction of rotation is negative, 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 directions of rotation are both positive. At this time, the direction of rotation of the rotational speed N6 of the output member (9) is negative. In order to avoid the situation where the direction of rotation 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 direction of rotation 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 be only positive and not negative, so that the direction of rotation of the rotational speed N6 of the output member (9) is always positive.

6. The speed change method of the dual-drive four-planetary-gear continuously variable transmission mechanism according to claim 2, characterized in that, 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 directions of rotation are both positive, so that the rotational speed N6 of the output member (9) is equal to the rotational speeds N1 of the first driving member and N2 of the second driving member, and the directions of rotation are both positive. At this time, the transmission ratio is 1.

7. The speed change method of the dual-drive four-planetary-gear continuously variable transmission mechanism according to claim 2, characterized in that 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 directions of rotation are both positive, so that the rotational speed N6 of the output member (9) is greater than the rotational speeds N1 of the first driving member and N2 of the second driving member, and the direction of rotation is positive.

8. The variable speed method of the dual-drive four-planetary-gear continuously variable transmission mechanism 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 positive. 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, making 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) zero. The rotational speed N6 of the output member (9) rotates in the positive direction, 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 dual-drive four-planetary-row continuously variable transmission mechanism 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 positive. 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, making 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) zero. The rotational speed N6 of the output member (9) rotates in the positive direction, 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).

Images