Three-planet gear continuously variable transmission mechanism with unilateral graded transmission and speed changing method thereof

Abstract

The three-planetary gear continuously variable transmission mechanism with unilateral graded transmission disclosed in the present invention and its speed change method belong to the technical field of continuously variable transmission, and include a first planetary gear, a second planetary gear, a third planetary gear and a transmission stage, wherein the transmission stage includes a transmission gear A and a transmission gear B, wherein the transmission gear A and the transmission gear B are meshed with external teeth, the first ring gear on the first planetary gear is connected with the second planetary carrier on the second planetary gear, the second planetary carrier on the second planetary gear is connected with the third sun gear on the third planetary gear through a connecting shaft, and the first planetary carrier on the first planetary gear is connected with the second ring gear on the second planetary gear and the third ring gear on the third planetary gear. A transmission stage is arranged between the first input shaft and the transmission shaft of the continuously variable transmission mechanism of the present invention, and the transmission stage achieves the purpose of changing the transmission ratio between the second driving member and the second sun gear by changing the gear ratio of the transmission gear A and the transmission gear B, thereby widening the power selection range of the second driving member.

Description

Technical Field

[0001] The present invention relates to the technical field of continuously variable transmission, and in particular to a three-planet gear continuously variable transmission mechanism with unilateral graded transmission and a speed changing method thereof. Background Art

[0002] As society's requirements for environmental protection become higher and higher, electric vehicle technology has become the mainstream research direction of major automakers. At present, electric vehicles mostly use fixed-speed ratio reducers. Although large-speed ratio reducers can be used to meet the power requirements of the vehicle when starting and climbing, the large speed ratio limits the vehicle from reaching a higher maximum speed. This is also the reason why the maximum speed of electric vehicles on the market is generally lower than that of fuel vehicles. In order to take into account the maximum speed and climbing ability of the vehicle, many automakers have begun to install AMT transmissions on electric vehicles. However, AMT transmissions are step-shifted in principle, and there are inherent problems of gear shifting and power interruption; the transmission ratio range of AMT transmissions is limited by the gear setting. In order to expand the transmission ratio range, it is necessary to set a lot of gears when applied to heavy vehicles. The gear shifting process is slow and the operation is complicated, which makes many truck drivers unwilling to step on the brakes; the gear shifting process of AMT transmissions relies on complex control strategies, and it is difficult to grasp the accurate gear shifting timing, resulting in high energy consumption and low efficiency; the structure of AMT transmissions is complex, the manufacturing cost is high, and maintenance is difficult. Summary of the invention

[0003] The purpose of the present invention is to solve the above problems and to design a three-planet gear continuously variable speed mechanism with unilateral graded transmission and a speed changing method thereof.

[0004] To achieve the above-mentioned purpose, the technical solution of the present invention is a three-planet row continuously variable transmission mechanism with unilateral graded transmission, comprising a first planet row, a second planet row, a third planet row and a transmission stage, wherein the transmission stage comprises a transmission gear A and a transmission gear B, wherein the transmission gear A and the transmission gear B are meshed by external teeth, the first ring gear on the first planet row is connected to the second planet carrier on the second planet row, the second planet carrier is connected to the third sun gear on the third planet row through a connecting shaft, the first planet carrier on the first planet row is connected to the second ring gear on the second planet row and the third ring gear on the third planet row, a one-way stopper is arranged on the connecting body of the first planet carrier, the second ring gear and the third ring gear, the third planet carrier on the third planet row is connected to an output component, the transmission shaft connected to the second sun gear on the second planet row passes through the second planet carrier, the connecting shaft, the third sun gear, the third planet carrier and the output component to be connected to the transmission gear B, the first input shaft connected to the first sun gear on the first planet row passes through the second sun gear, the transmission shaft and the transmission gear B to be connected to the first driving member, and the transmission gear A is connected to the second driving member through the second input shaft.

[0005] As a further illustration of the present invention, the first sun gear is meshed with a first planetary gear on its outer teeth, the first planetary gear is mounted on the first planet carrier, and the first planetary gear is meshed with an inner ring gear of the first gear ring;

[0006] The second sun gear has outer teeth meshed with second planetary gears, the second planetary gears are mounted on the second planet carrier, and the second planetary gears are meshed with inner ring teeth of the second gear ring;

[0007] The third sun gear is meshed with the outer teeth of the third planetary gear, the third planetary gear is mounted on the third planet carrier, and the third planetary gear is meshed with the inner ring teeth of the third gear ring.

[0008] As a further explanation of the present invention, the one-way stopper is used to limit the rotation direction of the first planetary carrier, the second ring gear and the third ring gear, and the one-way stopper makes the rotation direction of the first planetary carrier, the second ring gear and the third ring gear only consistent with the rotation direction of the second sun gear driven by the second drive member.

[0009] The present invention also provides a speed changing method of a three-planetary gear continuously variable transmission mechanism based on unilateral graded transmission, wherein the first driving member and the first sun gear are connected through a first input shaft, so that the rotational speed of the first driving member is the same as the rotational speed of the first sun gear; the second driving member and the second sun gear are connected through a second input shaft, a transmission stage, and a transmission shaft, so that the rotational speed of the second driving member and the rotational speed of the second sun gear are in a transmission ratio relationship of the transmission stage; the first planetary carrier, the second gear ring and the third gear ring are connected, so that the rotational speeds of the first planetary carrier, the second gear ring and the third gear ring are the same; the first gear ring, the second planetary carrier and the third sun gear are connected, so that the rotational speeds of the first gear ring, the second planetary carrier and the third sun gear are the same; the output component is connected to the third planetary carrier, so that the rotational speeds of the third planetary carrier and the output component are the same; by adjusting and controlling the rotational speeds of the first driving member and the second driving member, the stepless and continuous change of the rotational speed of the output component is realized, and in this process, the speed ratio will also change accordingly.

[0010] As a further explanation of the present invention, it is assumed that: the rotational speed of the first driving member and the rotational speed of the first sun gear are N1, the rotational speed of the second sun gear is N2, the transmission ratio of the transmission stage is i, the rotational speed of the second driving member is N2×i, the rotational speed of the first ring gear, the second planetary carrier and the third sun gear is N3, the rotational speed of the first planetary carrier, the second ring gear and the third ring gear is N4, the rotational speed of the third planetary carrier and the output member is N5, the number of teeth of the first sun gear is Z1, the number of teeth of the first ring gear is Z2, the number of teeth of the second sun gear is Z3, the number of teeth of the second ring gear is is Z4, the number of teeth of the third sun gear is Z5, the number of teeth of the third ring gear is Z6, when any two values ​​of N1, N2, N3, N4 and N5 are determined, the other three values ​​can be calculated through the proportional relationship of the line segments in the vector diagram; by driving the first driving member and the second driving member to adjust and control the rotational speed N1 of the first sun gear and the rotational speed N2 of the second sun gear, the continuous stepless change of the rotational speed N5 of the output component can be achieved; by adjusting and controlling the rotational speed N1 of the first sun gear and the rotational speed N2 of the second sun gear, the output state of the output component includes state A, state B, state C, state D and state E.

[0011] As a further explanation of the present invention, in the state A, the first driving member drives the first sun gear at a speed of N1, and the direction is reverse; the second driving member drives the second sun gear at a speed of N2, and the direction is forward; the ratio of the speed N2 of the second sun gear to the speed N1 of the first sun gear is equal to [Z1×(Z3+Z4)] / (Z2×Z3), the speed N4 of the first planetary carrier, the second ring gear and the third ring gear is 0, and the speed N5 of the output component is forward.

[0012] As a further explanation of the present invention, in the state B, the first driving member drives the first sun gear at a speed of N1, and the direction is reverse; the second driving member drives the second sun gear at a speed of N2, and the direction is forward; the ratio of the speed N2 of the second sun gear to the speed N1 of the first sun gear is greater than [Z1×(Z3+Z4)] / (Z2×Z3), the speed N4 of the first planetary carrier, the second ring gear and the third ring gear is in the forward direction, and the speed N5 of the output component is in the forward direction.

[0013] As a further explanation of the present invention, in the state C, the first driving member drives the first sun gear at a speed of N1, and the direction is reverse; the second driving member drives the second sun gear at a speed of N2, and the direction is forward; the ratio of the speed N2 of the second sun gear to the speed N1 of the first sun gear is less than [Z1×(Z3+Z4)] / (Z2×Z3), the direction of the speed N4 of the first planetary carrier, the second ring gear and the third ring gear is reverse, and the direction of the speed N5 of the output component may be forward or reverse. In order to prevent this from happening, a one-way stopper is provided on the connector of the first planetary carrier, the second ring gear and the third ring gear to limit the direction of the speed N4 of the first planetary carrier, the second ring gear and the third ring gear to only be forward and not reverse, thereby ensuring that the direction of the speed N5 of the output component is always forward.

[0014] As a further explanation of the present invention, in the state D, the speed N1 of the first sun gear driven by the first driving member is 0; the speed N2 of the second sun gear driven by the second driving member is positive; the speed N4 of the first planetary carrier, the second ring gear and the third ring gear is positive, and the speed N5 of the output component is positive.

[0015] As a further illustration of the present invention, in the state E, the rotational speed N1 of the first driving member driving the first sun gear and the rotational speed N2 of the second driving member driving the second sun gear are the same in magnitude, and both are in positive direction; the rotational speed N4 of the first planetary carrier, the second ring gear and the third ring gear are the same in magnitude as the N1 and the N2, and both are in positive direction; the rotational speed N5 of the output component is the same in magnitude as the N1, N2 and N4, and both are in positive direction.

[0016] As a further explanation of the present invention, when the first driving member fails, the rotation speed of the second driving member is N2×i, and the direction is reverse; the rotation speed of the second sun gear is N2, and the direction is forward; the rotation speed N4 of the first planetary carrier, the second ring gear and the third ring gear has a reverse trend, and at this time the one-way stopper limits their reverse rotation, so that the rotation speed N4 of the first planetary carrier, the second ring gear and the third ring gear is 0, and the rotation speed N5 of the output component rotates forward, and the power of the second driving member is output through the transmission system, the second planetary gear and the third planetary gear through deceleration and torque increase, and the transmission ratio is i×[(Z3+Z4)×(Z5+Z6)] / (Z3×Z5).

[0017] As a further explanation of the present invention, when the second driving member fails, the first driving member drives the first sun gear at a speed N1 in the reverse direction, and the speed N4 of the first planetary carrier, the second ring gear and the third ring gear has a reverse trend. At this time, the one-way stopper limits the reverse rotation, so that the speed N4 of the first planetary carrier, the second ring gear and the third ring gear is 0, and the speed N5 of the output component rotates forward. The power of the first driving member is output through the first planetary gear row and the third planetary gear row with reduced speed and increased torque, and the transmission ratio is [Z2×(Z5+Z6)] / (Z1×Z5).

[0018] The three-planet gear continuously variable transmission mechanism with unilateral graded transmission and the speed change method thereof provided by the present invention realizes the continuously variable speed change of the output end by adjusting the rotation speed of the first driving member and the second driving member and changing the transmission ratio between the input end and the output end through the cooperation between the first planetary gear, the second planetary gear, the third planetary gear and the one-way stopper. The 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 speed change mechanism, so that the input and output of power are both at one end of the continuously variable speed change mechanism. Such a design can greatly improve the utilization rate of space and make the entire power equipment more reasonable in terms of arrangement and space utilization. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] Figure 1 It is a schematic diagram of a three-planet gear continuously variable transmission mechanism with unilateral graded transmission provided by an embodiment of the present invention;

[0020] Figure 2 is a speed vector diagram of the first planetary gear provided by an embodiment of the present invention;

[0021] Figure 3 is a speed vector diagram of the second planetary gear provided by an embodiment of the present invention;

[0022] Figure 4 is a speed vector diagram of the third planetary gear provided by an embodiment of the present invention;

[0023] Figure 5 The embodiment of the present invention provides Figure 2 , Figure 3 , Figure 4 Merged tachogram;

[0024] Figure 6 is a speed vector diagram when the speed N4 of the first planet carrier, the second ring gear and the third ring gear is 0 provided by an embodiment of the present invention;

[0025] Figure 7is a speed vector diagram when the speed N4 of the first planet carrier, the second ring gear and the third ring gear provided by the embodiment of the present invention is less than 0;

[0026] Figure 8 is a speed vector diagram when the speed N1 of the first driving member provided by an embodiment of the present invention is 0;

[0027] Fig. 9 is a speed vector diagram when the speeds of the first sun gear and the second sun gear provided by an embodiment of the present invention are the same;

[0028] Fig.10 is a speed vector diagram provided by an embodiment of the present invention when the rotational directions of the speeds N1 and N2 of the first sun gear and the second sun gear are both forward at the same time;

[0029] Fig.11 is a speed vector diagram when the speed N4 of the first planet carrier, the second ring gear and the third ring gear is 0 under the reversing condition provided by an embodiment of the present invention;

[0030] Fig.12 is a speed vector diagram when the speed N4 of the first planet carrier, the second ring gear and the third ring gear is less than 0 under the reversing condition provided by an embodiment of the present invention;

[0031] Fig.13 is a speed vector diagram provided by an embodiment of the present invention when the first driving member fails and the speed N2 of the second sun gear driven by the second driving member turns to the forward direction;

[0032] Fig.14 It is a speed vector diagram provided by an embodiment of the present invention when the second driving member fails and the speed N1 of the first driving member turns to the reverse direction.

[0033] Reference numerals:

[0034] 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-transmission stage, 401-transmission gear A, 402-transmission gear B, 5-one-way stopper, 6-first input shaft, 7-second input shaft, 8-connecting shaft, 9-output component, 10-transmission shaft. DETAILED DESCRIPTION

[0035] First of all, we would like to explain the purpose of declaring the embodiment of the present invention. Our purpose is to solve the problems of gear shifting and power interruption inherent in the AMT transmission. The transmission ratio range of the AMT transmission is restricted by the gear setting. When used in heavy-duty vehicles, in order to expand the transmission ratio range, a large number of gears need to be set. The gear shifting process is slow and the operation is complicated, which leads to many truck drivers being unwilling to step on the brakes. The gear shifting process of the AMT transmission relies on complex control strategies, and it is difficult to grasp the accurate gear shifting timing, resulting in high energy consumption and low efficiency. The AMT transmission has existing problems such as complex structure, high manufacturing cost and difficult maintenance. Therefore, a three-planetary gearbox continuously variable transmission mechanism with unilateral graded transmission is proposed to solve the existing problems.

[0036] The embodiment of the present invention is described in detail below with reference to the accompanying drawings. We first introduce the specific structure of the embodiment of the present invention.

[0037] See also Figure 1 A three-planet row continuously variable transmission mechanism with unilateral graded transmission includes a first planet row 1, a second planet row 2, a third planet row 3 and a transmission stage 4, wherein the transmission stage 4 includes a transmission gear A401 and a transmission gear B402, wherein the transmission gear A401 and the transmission gear B402 are meshed with external teeth, wherein a first ring gear 103 on the first planet row 1 is connected to a second planet carrier 202 on the second planet row 2, wherein the second planet carrier 202 on the second planet row 2 is connected to a third sun gear 301 on the third planet row 3 via a connecting shaft 8, wherein the first planet carrier 102 on the first planet row 1 is connected to the second ring gear 203 on the second planet row 2 and the third ring gear 303 on the third planet row 3 ... A one-way stopper 5 is arranged on the connecting body of a planet carrier 102, a second ring gear 203 and a third ring gear 303; the third planet carrier 302 on the third planetary row 3 is connected with an output component 9; the transmission shaft 10 connected with the second sun gear 201 on the second planetary row 2 passes through the second planet carrier 202, the connecting shaft 8, the third sun gear 301, the third planet carrier 302 and the output component 9 to be connected with the transmission gear B402; the first input shaft 6 connected with the first sun gear 101 on the first planetary row 1 passes through the second sun gear 201, the transmission shaft 10 and the transmission gear B402 to be connected with the first driving member; and the transmission gear A401 on the transmission stage 4 is connected with the second driving member through the second input shaft 7.

[0038] See also Figure 1The first sun gear 101 meshes with the first planetary gear on its outer teeth, the first planetary gear is mounted on the first planet carrier 102, and the first planetary gear meshes with the inner ring teeth of the first ring gear 103; the second sun gear 201 meshes with the second planetary gear on its outer teeth, the second planetary gear is mounted on the second planet carrier 202, and the second planetary gear meshes with the inner ring teeth of the second ring gear 203; the third sun gear 301 meshes with the third planetary gear on its outer teeth, the third planetary gear is mounted on the third planet carrier 302, and the third planetary gear meshes with the inner ring teeth of the third ring gear 303.

[0039] See also Figure 1 The one-way stopper 5 is used to limit the rotation direction of the first planet carrier 102, the second ring gear 203 and the third ring gear 303. The one-way stopper 5 makes the rotation direction of the first planet carrier 102, the second ring gear 203 and the third ring gear 303 only consistent with the rotation direction of the second sun gear.

[0040] Next, we need to explain a speed changing method of a three-planet gear continuously variable speed changing mechanism based on unilateral graded transmission in combination with the specific structure of an embodiment of the present invention.

[0041] According to the basic principle of planetary gears, among the three components of the sun gear, ring gear and planetary carrier, if the speed of any two components is determined, the speed of another component is also determined, and their speed relationship is in a corresponding proportional relationship according to the number of sun gear teeth and the number of ring gear teeth.

[0042] According to the basic principle of planetary gears, if the rotation speed of any two of the three components, the sun gear, the ring gear and the planetary carrier, is the same, the rotation speed of the other component will also be the same.

[0043] Therefore, the rotational speed of the first driving member is the same as the rotational speed of the first sun gear 101, which is set to N1; the rotational speed of the second driving member is set to N2×i, and the rotational speed of the second sun gear 201 is N2; the rotational speeds of the first ring gear 103, the second planetary carrier 202 and the third sun gear 301 are the same, which is set to N3; the rotational speeds of the first planetary carrier 102, the second ring gear 203 and the third ring gear 303 are the same, which is set to N4; the rotational speeds of the third planetary carrier 302 and the output component 9 are the same, which is set to N5; the number of teeth of the first sun gear 101 is set to Z1, the number of teeth of the first ring gear 103 is set to Z2, the number of teeth of the second sun gear 201 is set to Z3, the number of teeth of the second ring gear 203 is set to Z4, the number of teeth of the third sun gear 301 is set to Z5, and the number of teeth of the third ring gear 303 is set to Z6.

[0044] According to the planetary gear speed vector calculation method, the speed vector diagram of the first planetary gear row 1 is obtained, as shown in Figure 2As shown. N1 is the speed of the first sun gear 101, N3 is the speed of the first ring gear 103, and N4 is the speed of the first planet carrier 102. The lengths of N1, N3, and N4 represent the speeds, and the arrow direction represents the speed direction. An upward arrow represents a positive speed, and a downward arrow represents a reverse speed. Set L2 / L3 = Z1 / Z2.

[0045] According to the speed vector calculation method of the planetary gear, the speed vector diagram of the second planetary gear 2 is obtained, as shown in Figure 3 As shown. N2 is the speed of the second sun gear 201, N4 is the speed of the second ring gear 203, and N3 is the speed of the second planet carrier 202. The lengths of N2, N3, and N4 represent the speeds, and the arrow direction represents the speed direction. An upward arrow represents a positive speed, and a downward arrow represents a reverse speed. Set L2 / L1=Z3 / Z4.

[0046] According to the speed vector calculation method of the planetary gear, the speed vector diagram of the third planetary gear 3 is obtained, as shown in Figure 4 As shown. N3 is the speed of the third sun gear 301, N4 is the speed of the third ring gear 303, and N5 is the speed of the third planet carrier 302. The lengths of N3, N4, and N5 represent the speeds, and the arrow direction represents the speed direction. An upward arrow represents a positive speed, and a downward arrow represents a reverse speed. Set L5 / L4=Z5 / Z6.

[0047] exist Figure 2 , Figure 3 and Figure 4 In the calculation, L1, L2, L3, L4, and L5 only need to satisfy the corresponding proportional relationship. The actual lengths of L1, L2, L3, L4, and L5 do not affect the calculation of the sizes of N1, N2, N3, N4, and N5. Figure 2 , Figure 3 , Figure 4 Merge Figure 5 , let L2=L4+L5.

[0048] See also Figure 5 , N1 is the rotational speed of the first sun gear 101, that is, the rotational speed of the first driving member; N2 is the rotational speed of the second sun gear 201; N3 is the rotational speed of the first ring gear 103, the second planetary carrier 202 and the third sun gear 301; N4 is the rotational speed of the first planetary carrier 102, the second ring gear 203 and the third ring gear 303; N5 is the rotational speed of the third planetary carrier 302 and the output component 9.

[0049] If any two values ​​of N1, N2, N3, N4 and N5 are determined, the other three values ​​can be calculated by the proportional relationship of the line segments in the vector diagram. That is, if the speed N1 of the first sun gear 101 is determined and the speed N2 of the second sun gear 201 is determined, then the speed N5 of the output component 9 is also uniquely determined. By adjusting and controlling the speed N1 of the first sun gear 101 and the speed N2 of the second sun gear 201 by the first driving member and the second driving member, the speed N5 of the output component 9 can be continuously and steplessly changed.

[0050] The speed change principle of the three-planet gear continuously variable transmission mechanism with unilateral graded transmission in the embodiment of the present invention is explained below in combination with specific working conditions.

[0051] 1. Starting conditions

[0052] See also Figure 5 and Figure 6 When starting, the first driving member drives the first sun gear 101 at a speed of N1 and a reverse direction; the second driving member drives the second sun gear 201 at a speed of N2 and a forward direction. The two driving members start to accelerate at the same time, and the ratio of the speed N2 of the second sun gear 201 to the speed N1 of the first sun gear 101 is always greater than (such as Figure 5 ) or equal to (such as Figure 6 )[Z1×(Z3+Z4)] / (Z2×Z3), the speed N5 of the output component 9 can be gradually accelerated from 0 and turned to the positive direction. Under this working condition, the transmission ratio is the largest, the power of the first driving member and the second driving member are coupled together, the torque output is increased, and the vehicle accelerates forward.

[0053] 2. Acceleration and deceleration conditions

[0054] The acceleration and deceleration process can be divided into three situations according to the direction of the rotation speed N1 of the first driving member, specifically including:

[0055] 1) Case 1

[0056] See also Figure 5 and Figure 6 , the first driving member drives the first sun gear 101 at a speed of N1, and the direction of rotation is reverse; the second driving member drives the second sun gear 201 at a speed of N2, and the direction of rotation is forward. By controlling the ratio of the speed N2 of the second sun gear 201 to the speed N1 of the first sun gear 101 to always be greater than or equal to [Z1×(Z3+Z4)] / (Z2×Z3). By controlling the speed of increase or decrease of the speed N1 of the first sun gear 101 and the speed N2 of the second sun gear 201 by the first driving member and the second driving member, it is possible to control the speed N5 of the output component 9 to gradually increase or decrease, and the direction of rotation is forward, so that the vehicle accelerates or decelerates to move forward.

[0057] 2) Case 2

[0058] See also Figure 8 The first driving member drives the first sun gear 101 at a speed of N1, which gradually decreases to 0. The second driving member drives the second sun gear 201 at a speed of N2, and the steering is positive. By controlling the speed N1 of the first sun gear 101 to 0 and the speed N2 of the second sun gear 201 to increase or decrease, the output speed N5 can be gradually increased or decreased, and the steering is positive, so that the vehicle accelerates or decelerates to move forward.

[0059] 3) Case 3

[0060] See also Fig.10 The first driving member drives the first sun gear 101 at a speed of N1, and the direction of rotation is positive, and the second driving member drives the second sun gear 201 at a speed of N2, and the direction of rotation is positive. By controlling the speed of increase or decrease of the speed N1 of the first sun gear 101 and the speed N2 of the second sun gear 201 by the first driving member and the second driving member, the output speed N5 can be gradually increased or decreased, and the direction of rotation is positive, so that the vehicle accelerates or decelerates to move forward.

[0061] In addition, the speed regulation method for acceleration and deceleration can also be to maintain the speed N1 of the first driving member unchanged, and adjust the speed N5 of the output component 9 by adjusting the speed N2×i of the second driving member; or the speed N2×i of the second driving member can be maintained unchanged, and the speed N5 of the output component 9 can be adjusted by adjusting the speed N1 of the first driving member. In the process of accelerating or decelerating the speed N5 of the output component 9, the first driving member and the second driving member can be different according to their respective high-efficiency working areas, and the control system can control the acceleration, deceleration and maintenance of the speed of the first driving member and the second driving member according to the current working conditions. In this way, the first driving member and the second driving member can work in their respective high-efficiency working areas for a long time, thereby achieving energy saving.

[0062] 3. Maximum speed condition

[0063] See also Fig. 9 and Fig.10 , the first driving member drives the first sun gear 101 at a speed of N1, and the direction of rotation is forward, and the second driving member drives the second sun gear 201 at a speed of N2, and the direction of rotation is forward. When the speeds N1 of the first sun gear 101 and N2 of the second sun gear 201 both reach the maximum speed, the speed N5 of the output member 9 also reaches the maximum speed, and the vehicle speed reaches the maximum vehicle speed at this time. If the maximum speeds of the speeds N1 of the first sun gear 101 and N2 of the second sun gear 201 are the same, then the maximum speed that the speed N5 of the output member 9 can reach is also the same as the maximum speeds N1 and N2 of the first sun gear 101 and the second sun gear 201, and the transmission ratio is 1 at this time.

[0064] With respect to the above-mentioned starting conditions and acceleration and deceleration conditions, there is a dangerous condition that needs to be considered how to avoid.

[0065] Example: See Figure 7 , when the first driving member drives the first sun gear 101 to rotate in the reverse direction at a speed N1, and the second driving member drives the second sun gear 201 to rotate in the forward direction at a speed N2, the vehicle is in the starting stage, or in the medium and low speed stage. If the speed control of the first driving member and the second driving member is inaccurate or the control fails, the ratio of the speed N2 of the second sun gear 201 to the speed N1 of the first sun gear 101 is less than [Z1×(Z3+Z4)] / (Z2×Z3), as Figure 7 As shown, the rotation speed N5 of the output component 9 may turn in the reverse direction. At this time, the vehicle suddenly reverses and a serious accident may occur. In order to prevent this from happening, a one-way stopper 5 is provided on the connecting body of the first planetary carrier 102, the second ring gear 203 and the third ring gear 303 to limit the rotation speed N4 of the first planetary carrier 102, the second ring gear 203 and the third ring gear 303 to only be forward and not reverse. In this way, it is ensured that the rotation speed N5 of the output component 9 is always forward. Therefore, when this dangerous working condition occurs, since the one-way stopper 5 limits the rotation speed N4 of the first planetary carrier 102, the second ring gear 203 and the third ring gear 303 to only be forward and not reverse, the two driving members will drag each other at this time, and the ratio of the rotation speed N2 of the second sun gear 201 to the rotation speed N1 of the first sun gear 101 will always be equal to [Z1×(Z3+Z4)] / (Z2×Z3). The rotation speed N4 of the first planetary carrier 102, the second ring gear 203 and the third ring gear 303 is equal to 0, and the rotation speed N5 of the output component 9 can only be turned in the forward direction, so reverse driving will not occur suddenly.

[0066] 4. Reversing conditions

[0067] See also Fig.11 and Fig.12 When reversing, the first driving member drives the first sun gear 101 at a speed of N1, and the direction is forward, and the second driving member drives the second sun gear 201 at a speed of N2, and the direction is reverse. The two driving members start to accelerate at the same time, and the ratio of the speed N2 of the second sun gear 201 to the speed N1 of the first sun gear 101 is always greater than (such as Fig.12 ) or equal to (such as Fig.11)[Z1×(Z3+Z4)] / (Z2×Z3), the rotation speed N5 of the output component 9 can be controlled to gradually accelerate from 0 and turn to the reverse direction. If the rotation speed control of the first driving member and the second driving member is inaccurate or the control fails, when the ratio of the rotation speed N2 of the second sun gear 201 to the rotation speed N1 of the first sun gear 101 is less than [Z1×(Z3+Z4)] / (Z2×Z3), the rotation speed N5 of the output component 9 may turn to the forward direction. At this time, the vehicle suddenly moves forward, which is very likely to cause a serious accident. In order to prevent this from happening, a one-way stopper 5 is provided on the connecting body of the first planetary carrier 102, the second ring gear 203 and the third ring gear 303 to limit the rotation speed N4 of the first planetary carrier 102, the second ring gear 203 and the third ring gear 303 to only turn to the reverse direction, not the forward direction. In this way, it is ensured that the rotation speed N5 of the output component 9 is always turned to the reverse direction.

[0068] In addition to the normal operating conditions and dangerous operating conditions mentioned above, there are also some emergency operating conditions that need to be dealt with, which are taken into consideration and resolved in the embodiments of the present invention.

[0069] Example: See Fig.13 When the first driving member fails, the rotation speed of the second driving member is N2×i, the direction of rotation is positive, and the rotation speed N4 of the first planetary carrier 102, the second ring gear 203 and the third ring gear 303 has a reverse trend. At this time, the one-way stopper 5 limits the reverse rotation, so that the rotation speed N4 of the first planetary carrier 102, the second ring gear 203 and the third ring gear 303 is 0, and the rotation speed N5 of the output component 9 rotates forward. The power of the second driving member is output through the transmission stage, the second planetary gear 2 and the third planetary gear 3 with deceleration and torque increase. The transmission ratio is i×[(Z3+Z4)×(Z5+Z6) / Z3×Z5], so that the vehicle can continue to accelerate or decelerate and move forward.

[0070] See also Fig.14 When the second driving member fails, the rotation speed of the first driving member is N1, the direction is reverse, and the rotation speed N4 of the first planetary carrier 102, the second ring gear 203 and the third ring gear 303 tends to reverse. At this time, the one-way stopper 5 limits the reverse rotation, so that the rotation speed N4 of the first planetary carrier 102, the second ring gear 203 and the third ring gear 303 is 0, and the rotation speed N5 of the output component 9 rotates forward. The power of the first driving member is output through the first planetary gear 1 and the third planetary gear 3 with deceleration and torque increase, and the transmission ratio is [Z2×(Z5+Z6)] / (Z1×Z5), so that the vehicle can continue to accelerate or decelerate and move forward.

[0071] It can be seen that when one driving component fails, the other driving component can still drive the vehicle. Although the power is reduced, the vehicle can be driven to a maintenance location or a safe place by relying on one driving component, which can greatly improve the reliability of the vehicle.

[0072] The three-planet gear continuously variable transmission mechanism with unilateral graded transmission and the speed change method thereof provided in the embodiment of the present invention have the following advantages:

[0073] 1. The three-planet gear continuously variable transmission mechanism with unilateral graded transmission in the embodiment of the present invention has no power interruption during the speed regulation process and runs quietly and smoothly. Users will have a better car experience when using the car, which can greatly meet customer needs in terms of sensory perception and lay a very good foundation for the promotion and use of this product.

[0074] 2. The three-planet gear continuously variable transmission mechanism with unilateral graded transmission in the embodiment of the present invention can achieve large torque at the output end from low speed to high speed. By outputting large torque, the vehicle can have the ability to quickly accelerate and start when driving. The large torque can help the vehicle climb a larger slope when climbing a slope. The large torque can also meet the car use needs of more people, making this product more popular.

[0075] 3. The three-planet gear continuously variable transmission mechanism with unilateral graded transmission in the embodiment of the present invention can realize stepless and continuous change of output speed, and the input end drive element can work in the high-efficiency range for a long time, thereby improving work efficiency, achieving more economical effect in energy use, and making more contributions to energy saving.

[0076] 4. The three-planet gear continuously variable transmission mechanism with unilateral graded transmission in the embodiment of the present invention has the advantages of simple and convenient speed regulation. It only needs to control the rotation speed of the first driving member and the second driving member to achieve stepless and continuous change of the output rotation speed, thereby reducing the vehicle's requirements for the control system, making the promotion and use scope of this product wider, and ensuring the promotion and popularity of this product to a certain extent.

[0077] 5. In the embodiment of the present invention, the power of the first driving member and the second driving member are coupled together to drive the vehicle. When one of the driving members fails, the other driving member can still continue to drive the vehicle, ensuring that when the car owner is using the car, even if one driving member fails, the car owner can still rely on the other driving member to drive the car and drive the car to the maintenance site in time, avoiding the need to call a tow truck and better taking care of the car owner's car experience.

[0078] 6. Compared with the traditional single drive component driving mode, the product using the embodiment of the present invention can not only be driven by dual drive components, but also can select drive components with smaller volume and lower rotation speed to match. The small-volume drive components are more conducive to the layout design of the drive components in the vehicle body, and more convenient for the aesthetic design of the later vehicle body appearance. The use of smaller drive components can save costs.

[0079] 7. The three-planet gear continuously variable transmission mechanism with unilateral graded transmission in the embodiment of the present invention has a high efficiency transmission rate. Under the same working conditions, a motor with lower power and lower speed can be selected as a driving part. Compared with a high-power battery, a low-power battery can better prevent the occurrence of battery overheating. The safety of battery use is indirectly improved through the embodiment of the present invention.

[0080] 8. The three-planet gear continuously variable transmission mechanism with unilateral graded transmission in the embodiment of the present invention adopts a three-planet gear transmission, which increases the transmission ratio and further increases the torque. It can be used in heavy vehicles such as trucks, muck trucks, and buses with larger loads, further broadening the scope of application of the embodiment of the present invention.

[0081] 9. The three-planetary gear continuously variable transmission mechanism with unilateral graded transmission in the embodiment of the present invention sets the connection ends of the first drive member, the second drive member and the output member 9 at one end of the continuously variable transmission, so that the input and output of power are both at one end of the continuously variable transmission mechanism. Such a design can greatly improve the utilization of space and make the entire power equipment more reasonable in layout and space utilization.

[0082] 10. The three-planetary gear continuously variable transmission mechanism with unilateral graded transmission in the embodiment of the present invention is provided with a transmission stage 4 between the second input shaft 7 and the transmission shaft 10. The transmission stage 4 changes the gear ratio of the transmission gear A401 and the transmission gear B402 to achieve the purpose of changing the transmission ratio between the second driving member and the second sun gear 201. Therefore, under the premise of achieving the same use effect, the transmission ratio provided by the transmission stage 4 broadens the power selection range of the second driving member.

[0083] The above technical solutions only reflect the preferred technical solutions of the technical solutions of the present invention. Some changes that may be made to certain parts thereof by technicians in this technical field all reflect the principles of the present invention and fall within the protection scope of the present invention.

Claims

1. A three-planet gear continuously variable transmission mechanism with unilateral graded transmission, characterized in that: The invention comprises a first planetary row (1), a second planetary row (2), a third planetary row (3) and a transmission stage (4), wherein the transmission stage (4) comprises a transmission gear A (401) and a transmission gear B (402), wherein the transmission gear A (401) and the transmission gear B (402) are meshed with each other via external teeth, wherein a first ring gear (103) on the first planetary row (1) is connected to a second planetary carrier (202) on the second planetary row (2), wherein the second planetary carrier (202) is connected to a third sun gear (301) on the third planetary row (3) via a connecting shaft (8), wherein the first planetary carrier (102) on the first planetary row (1) is connected to a second ring gear (203) on the second planetary row (2) and a third ring gear (303) on the third planetary row (3), wherein the first planetary carrier (102) and the second ring gear ( A one-way stopper (5) is provided on a connecting body of the third planetary gear (203) and the third ring gear (303); the third planetary carrier (302) on the third planetary gear (3) is connected to an output component (9); a transmission shaft (10) connected to the second sun gear (201) on the second planetary gear (2) passes through the second planetary carrier (202), the connecting shaft (8), the third sun gear (301), the third planetary carrier (302) and the output component (9) to be connected to the transmission gear B (402); a first input shaft (6) connected to the first sun gear (101) on the first planetary gear (1) passes through the second sun gear (201), the transmission shaft (10) and the transmission gear B (402) to be connected to the first driving component; and the transmission gear A (401) is connected to the second driving component via a second input shaft (7); The first sun gear (101) is meshed with a first planetary gear on its outer teeth, the first planetary gear is mounted on the first planet carrier (102), and the first planetary gear is meshed with an inner ring gear of the first ring gear (103); The second sun gear (201) is meshed with a second planetary gear on its outer teeth, the second planetary gear is mounted on the second planet carrier (202), and the second planetary gear is meshed with an inner ring gear of the second ring gear (203); The third sun gear (301) is meshed with a third planetary gear on its outer teeth, the third planetary gear is mounted on the third planet carrier (302), and the third planetary gear is meshed with the inner ring teeth of the third gear ring (303); The one-way stopper (5) is used to limit the rotation direction of the first planet carrier (102), the second ring gear (203) and the third ring gear (303). The one-way stopper (5) makes the rotation direction of the first planet carrier (102), the second ring gear (203) and the third ring gear (303) only consistent with the rotation direction of the second sun gear (201) connected to the second driving member.

2. A speed changing method of the three-planet gear continuously variable speed changing mechanism with unilateral graded transmission according to claim 1, characterized in that: The first driving member and the first sun gear (101) are connected via a first input shaft (6), so that the rotation speed of the first driving member is the same as the rotation speed of the first sun gear (101); the second driving member and the second sun gear (201) are connected via a second input shaft (7), a transmission stage (4), and a transmission shaft (10), so that the rotation speed of the second driving member and the rotation speed of the second sun gear (201) are in a transmission ratio relationship of the transmission stage (4); the first planet carrier (102), the second ring gear (203), and the third ring gear (303) are connected, so that the first planet carrier (102), the second ring gear (203) ) and the third ring gear (303) have the same rotational speed; the first ring gear (103), the second planetary carrier (202) and the third sun gear (301) are connected so that the first ring gear (103), the second planetary carrier (202) and the third sun gear (301) have the same rotational speed; the output component (9) is connected to the third planetary carrier (302) so that the third planetary carrier (302) and the output component (9) have the same rotational speed; by adjusting and controlling the rotational speed of the first driving component and the rotational speed of the second driving component, the rotational speed of the output component (9) is continuously changed, and in this process, the speed ratio will also change accordingly.

3. The speed changing method of the three-planet gear continuously variable transmission mechanism with unilateral graded transmission according to claim 2, characterized in that: Assume that: the rotational speed of the first driving member and the rotational speed of the first sun gear (101) are N1, the rotational speed of the second sun gear (201) is N2, the transmission ratio of the transmission stage (4) is i, the rotational speed of the second driving member is N2×i, the rotational speed of the first ring gear (103), the second planet carrier (202) and the third sun gear (301) is N3, the rotational speed of the first planet carrier (102), the second ring gear (203) and the third ring gear (303) is N4, the rotational speed of the third planet carrier (302) and the output member (9) is N5, the number of teeth of the first sun gear (101) is Z1, the number of teeth of the first ring gear (103) is Z2, the number of teeth of the second sun gear (201) is Z3, the The number of teeth of the second gear ring (203) is Z4, the number of teeth of the third sun gear (301) is Z5, and the number of teeth of the third gear ring (303) is Z6. When any two values ​​of N1, N2, N3, N4 and N5 are determined, the other three values ​​can be calculated through the proportional relationship of the line segments in the vector diagram; by driving the first driving member and the second driving member to adjust and control the rotation speed N1 of the first sun gear (101) and the rotation speed N2 of the second sun gear (201), the rotation speed N5 of the output component (9) can be continuously and steplessly changed; by adjusting and controlling the rotation speed N1 of the first sun gear (101) and the rotation speed N2 of the second sun gear (201), the output state of the output component (9) includes state A, state B, state C, state D and state E.

4. The speed changing method of the three-planet gear continuously variable transmission mechanism with unilateral graded transmission according to claim 3, characterized in that: In the state A, the first driving member drives the first sun gear (101) at a speed of N1, and the direction of rotation is reverse; the second driving member drives the second sun gear (201) at a speed of N2, and the direction of rotation is forward; the ratio of the speed N2 of the second sun gear (201) to the speed N1 of the first sun gear (101) is equal to [Z1×(Z3+Z4)] / (Z2×Z3), the speed N4 of the first planetary carrier (102), the second ring gear (203) and the third ring gear (303) is 0, and the direction of rotation of the speed N5 of the output component (9) is forward.

5. The speed changing method of the three-planet gear continuously variable transmission mechanism with unilateral graded transmission according to claim 3, characterized in that: In the state B, the first driving member drives the first sun gear (101) at a rotational speed of N1, and the direction of rotation is reverse; the second driving member drives the second sun gear (201) at a rotational speed of N2, and the direction of rotation is forward; the ratio of the rotational speed N2 of the second sun gear (201) to the rotational speed N1 of the first sun gear (101) is greater than [Z1×(Z3+Z4)] / (Z2×Z3), the rotational speed N4 of the first planetary carrier (102), the second ring gear (203) and the third ring gear (303) is forward, and the rotational speed N5 of the output component (9) is forward.

6. The speed changing method of the three-planet gear continuously variable transmission mechanism with unilateral graded transmission according to claim 3, characterized in that: In the state C, the first driving member drives the first sun gear (101) at a speed of N1, and the direction of rotation is reverse; the second driving member drives the second sun gear (201) at a speed of N2, and the direction of rotation is forward; the ratio of the speed N2 of the second sun gear (201) to the speed N1 of the first sun gear (101) is less than [Z1×(Z3+Z4)] / (Z2×Z3), and the first planet carrier (102), the second gear ring (203) and the third gear ring (303) are The rotational speed N4 is in the reverse direction, and the rotational speed N5 of the output component (9) is in the forward direction or the reverse direction. In order to prevent this from happening, a one-way stopper (5) is provided on the connecting body of the first planetary carrier (102), the second ring gear (203) and the third ring gear (303), so as to limit the rotational speed N4 of the first planetary carrier (102), the second ring gear (203) and the third ring gear (303) to only be in the forward direction and not in the reverse direction, thereby ensuring that the rotational speed N5 of the output component (9) is always in the forward direction.

7. The speed changing method of the three-planet gear continuously variable transmission mechanism with unilateral graded transmission according to claim 3, characterized in that: In the state D, the rotational speed N1 of the first sun gear (101) driven by the first driving member is 0; the rotational speed N2 of the second sun gear (201) driven by the second driving member is positive; the rotational speed N4 of the first planet carrier (102), the second ring gear (203) and the third ring gear (303) is positive, and the rotational speed N5 of the output member (9) is positive.

8. The speed changing method of the three-planet gear continuously variable transmission mechanism with unilateral graded transmission according to claim 3, characterized in that: In the state E, the rotational speed N1 of the first driving member driving the first sun gear (101) and the rotational speed N2 of the second driving member driving the second sun gear (201) are the same in magnitude, and the directions of rotation are both positive; the rotational speed N4 of the first planet carrier (102), the second ring gear (203) and the third ring gear (303) are the same in magnitude as the N1 and the N2, and the directions of rotation are both positive; the rotational speed N5 of the output component (9) is the same in magnitude as the N1, N2 and N4, and the directions of rotation are both positive.

9. The speed changing method of the three-planet gear continuously variable transmission mechanism with unilateral graded transmission according to claim 3, characterized in that: When the first driving member fails, the rotation speed of the second driving member is N2×i, and the direction of rotation is reverse; the rotation speed of the second sun gear (201) is N2, and the direction of rotation is forward; the rotation speed N4 of the first planetary carrier (102), the second ring gear (203) and the third ring gear (303) has a reverse trend; at this time, the one-way stopper (5) limits their reverse rotation, so that the rotation speed N4 of the first planetary carrier (102), the second ring gear (203) and the third ring gear (303) is 0; the rotation speed N5 of the output component (9) rotates forward; the power of the second driving member is output through the transmission stage (4), the second planetary gear (2) and the third planetary gear (3) to reduce speed and increase torque, and the transmission ratio is i×[(Z3+Z4)×(Z5+Z6)] / (Z3×Z5).

10. The speed changing method of the three-planet gear continuously variable speed changing mechanism with unilateral graded transmission according to claim 3, characterized in that: When the second driving member fails, the first driving member drives the first sun gear (101) to rotate at a speed N1 in the reverse direction, and the speed N4 of the first planetary carrier (102), the second ring gear (203) and the third ring gear (303) has a reverse rotation trend. At this time, the one-way stopper (5) limits the reverse rotation, so that the speed N4 of the first planetary carrier (102), the second ring gear (203) and the third ring gear (303) is 0, and the speed N5 of the output component (9) rotates in the positive direction. The power of the first driving member is output through the first planetary gear (1) and the third planetary gear (3) to reduce speed and increase torque, and the transmission ratio is [Z2×(Z5+Z6)] / (Z1×Z5).

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