A dual-drive three-planet gear continuously variable transmission mechanism and a speed changing method thereof

Abstract

The present invention discloses a dual-drive three-planetary gear continuously variable transmission mechanism, which belongs to the technical field of continuously variable transmission, and includes a first planetary gear, a second planetary gear and a third planetary gear, wherein the first ring gear on the first planetary gear is connected to the second planetary gear frame on the second planetary gear, the second planetary gear frame is connected to the third sun gear on the third planetary gear frame through a connecting shaft, the first planetary gear frame on the first planetary gear frame is connected to the second ring gear on the second planetary gear frame and the third ring gear on the third planetary gear frame, and a one-way stopper is arranged on the connecting body of the first planetary gear frame, the second ring gear and the third ring gear frame. The present invention also discloses a speed change method of the dual-drive three-planetary gear continuously variable transmission mechanism. The input end driving member of the continuously variable transmission mechanism of the present invention can always work in the high-efficiency zone to realize the continuously variable speed change at the output end, and 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.

Description

Technical Field

[0001] The present invention relates to the technical field of continuously variable transmissions, and in particular to a dual-drive three-planetary gear continuously variable transmission mechanism 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 dual-drive three-planetary gear continuously variable transmission mechanism and a transmission method thereof.

[0004] To achieve the above-mentioned purpose, the technical solution of the present invention is a dual-drive three-planetary gear continuously variable transmission mechanism, including a first planetary gear, a second planetary gear and a third planetary gear, the first ring gear on the first planetary gear is connected to the second planetary carrier on the second planetary gear, the second planetary carrier is connected to the third sun gear on the third planetary gear through a connecting shaft, the first planetary carrier on the first planetary gear is connected to the second ring gear on the second planetary gear and the third ring gear on the third planetary gear, a one-way stopper is arranged on the connecting body of the first planetary carrier, the second ring gear and the third ring gear, the third planetary carrier on the third planetary gear is connected with an output component, the first sun gear on the first planetary gear is connected to the first driving member through a first input shaft, and the second input shaft connected to the second sun gear on the second planetary gear passes through the first sun gear, the first input shaft and the first driving member to be connected to the second driving member.

[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 has outer teeth meshed with a third planetary gear, the third planetary gear is mounted on the third planet carrier, and the third planetary gear is meshed with 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 driving member.

[0009] The present invention also provides a speed changing method based on a dual-drive three-planetary gear continuously variable speed changing mechanism, 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, so that the rotational speed of the second driving member is the same as the rotational speed of the second sun gear; the first planetary carrier, the second ring gear and the third ring gear are connected, so that the rotational speeds of the first planetary carrier, the second ring gear and the third ring gear are the same; the first ring gear, the second planetary carrier and the third sun gear are connected, so that the rotational speeds of the first ring gear, 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 driving member and the rotational speed of the second sun gear are N2, the rotational speeds of the first ring gear, the second planet carrier and the third sun gear are N3, the rotational speeds of the first planet carrier, the second ring gear and the third ring gear are N4, the rotational speeds of the third planet carrier and the output member are 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 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 adjusting and controlling the rotational speed N1 of the first driving member and the rotational speed N2 of the second driving member, the continuous stepless change of the rotational speed N5 of the output member can be achieved; 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 state of the output member 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 direction of rotation of the rotational speed N1 of the first driving member is reverse, the direction of rotation of the rotational speed N2 of the second driving member is forward, the ratio of the rotational speed N2 of the second driving member to the rotational speed N1 of the first driving member is equal to [Z1×(Z3+Z4)] / (Z2×Z3), the rotational speed N4 of the first planetary carrier, the second ring gear and the third ring gear is 0, and the direction of rotation of the rotational speed N5 of the output member is forward.

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

[0013] As a further explanation of the present invention, in the state C, the rotational speed N1 of the first driving member turns in the reverse direction, the rotational speed N2 of the second driving member turns in the forward direction, the ratio of the rotational speed N2 of the second driving member to the rotational speed N1 of the first driving member is less than [Z1×(Z3+Z4)] / (Z2×Z3), the rotational speed N4 of the first planetary carrier, the second ring gear and the third ring gear turns in the reverse direction, and the rotational speed N5 of the output component may turn in the forward and reverse directions. 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 rotational 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 rotational speed N5 of the output component is always forward.

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

[0015] As a further explanation of the present invention, in the state E, the rotational speed N1 of the first driving member and the rotational speed N2 of the second driving member 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, and the transmission ratio of the state E is 1.

[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, the direction of rotation is positive, and the rotation 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 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. The power of the second driving member is output through the second planetary gear and the third planetary gear through deceleration and torque increase, and the transmission ratio is [(Z3+Z4)×(Z5+Z6)] / (Z3×Z5).

[0017] As a further explanation of the present invention, when the second driving member fails, the rotational speed of the first driving member is N1, and the direction is reverse. The rotational speed N4 of the first planetary carrier, the second ring gear and the third ring gear has a tendency to reverse. At this time, the one-way stopper limits the reverse rotation, so that the rotational speed N4 of the first planetary carrier, the second ring gear and the third ring gear is 0, and the rotational speed N5 of the output component rotates in the positive direction. The power of the first driving member is output through the first planetary gear set and the third planetary gear set to reduce speed and increase torque, and the transmission ratio is [(Z3+Z4)×(Z5+Z6)] / (Z3×Z5).

[0018] The dual-drive three-planetary gear continuously variable transmission mechanism and the speed change method provided by the present invention realize continuously variable speed change of the output end by adjusting the rotational speed of the first driving member and the second driving member and by cooperating 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. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] Figure 1 Schematic diagram of a dual-drive three-planetary gear continuously variable transmission mechanism 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 in 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 7 is a speed vector diagram when the speed N4 of the first planet carrier, the second ring gear and the third ring gear provided by an 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 driving member and the second driving member provided by the 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 directions of the speeds N1 and N2 of the first driving member and the second driving member are both positive;

[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 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 driving member turns to the positive 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-one-way stopper, 5-first input shaft, 6-second input shaft, 7-connecting shaft, 8-output component. 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 causes many truck drivers to be 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 dual-drive three-planetary gearbox continuously variable transmission mechanism 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 dual-drive three-planetary gear continuously variable transmission mechanism comprises a first planetary gear row 1, a second planetary gear row 2 and a third planetary gear row 3, the first ring gear 103 on the first planetary gear row 1 is connected to the second planetary gear carrier 202 on the second planetary gear row 2, the second planetary gear carrier 202 on the second planetary gear row 2 is connected to the third sun gear 301 on the third planetary gear row 3 through a connecting shaft 7, the first planetary gear carrier 102 on the first planetary gear row 1 is connected to the second ring gear 203 on the second planetary gear row 2 and the third ring gear 303 on the third planetary gear row 3, a one-way stopper 4 is arranged on the connecting body of the first planetary gear carrier 102, the second ring gear 203 and the third ring gear 303, the third planetary gear carrier 302 on the third planetary gear row 3 is connected to an output component 8, the first sun gear 101 on the first planetary gear row 1 is connected to the first driving member through a first input shaft 5, and the second input shaft 6 connected to the second sun gear 201 on the second planetary gear row 2 passes through the first sun gear 101, the first input shaft 5 and the first driving member to be connected to the second driving member.

[0038] See also Figure 1 The 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 4 is used to limit the rotation direction of the first planetary carrier 102, the second ring gear 203 and the third ring gear 303. The one-way stopper 4 makes the rotation direction of the first planetary carrier 102, the second ring gear 203 and the third ring gear 303 only consistent with the rotation direction of the second driving member.

[0040] Next, we need to explain a speed changing method based on a dual-drive three-planetary gear continuously variable transmission mechanism 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 the same as the rotational speed of the second sun gear 201, which is set to N2; the rotational speed of the first ring gear 103, the second planetary carrier 202 and the third sun gear 301 is the same, which is set to N3; the rotational speed of the first planetary carrier 102, the second ring gear 203 and the third ring gear 303 is the same, which is set to N4; the rotational speed of the third planetary carrier 302 and the output component 8 is 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 2 As 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 4In 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, that is, the rotational speed of the second driving member; 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 8.

[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 driving member is determined and the speed N2 of the second driving member is determined, then the speed N5 of the output member 8 is also uniquely determined. By adjusting and controlling the speed N1 of the first driving member and the speed N2 of the second driving member, the speed N5 of the output member 8 can be continuously and steplessly changed.

[0050] The speed change principle of the dual-drive three-planetary gear continuously variable transmission mechanism according to the embodiment of the present invention will be described below in conjunction with specific working conditions.

[0051] 1. Starting conditions

[0052] See also Figure 5 and Figure 6 When starting, the speed N1 of the first driving member turns to the reverse direction, and the speed N2 of the second driving member turns to the forward direction. The two driving members start to accelerate at the same time, and the ratio of the speed N2 of the second driving member to the speed N1 of the first driving member 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 8 can be controlled to gradually accelerate from 0 and turn 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 rotation speed N1 of the first driving member turns in the reverse direction, and the rotation speed N2 of the second driving member turns in the forward direction. The ratio of the rotation speed N2 of the second driving member to the rotation speed N1 of the first driving member is always greater than or equal to [Z1×(Z3+Z4)] / (Z2×Z3). By controlling the speed of increase or decrease of the rotation speed N1 of the first driving member and the rotation speed N2 of the second driving member, it is possible to control the rotation speed N5 of the output component 8 to gradually increase or decrease, turn in the forward direction, and accelerate or decelerate the vehicle to move forward.

[0057] 2) Case 2

[0058] See also Figure 8 , the rotational speed N1 of the first driving member gradually decreases to 0, and the rotational speed N2 of the second driving member turns to the positive direction. By controlling the rotational speed N1 of the first driving member to 0 and the speed of increase or decrease of the rotational speed N2 of the second driving member, the output rotational speed N5 can be gradually increased or decreased and turned to the positive direction, so that the vehicle accelerates or decelerates to move forward.

[0059] 3) Case 3

[0060] See also Fig.10 , the rotation speed N1 of the first driving member turns in the positive direction, and the rotation speed N2 of the second driving member turns in the positive direction. By controlling the speed of increase or decrease of the rotation speed N1 of the first driving member and the rotation speed N2 of the second driving member, the output rotation speed N5 can be gradually increased or decreased, and the rotation direction 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 rotation speed N1 of the first driving member unchanged, and adjust the rotation speed N5 of the output component 8 by adjusting the rotation speed N2 of the second driving member; or the rotation speed N2 of the second driving member can be maintained unchanged, and the rotation speed N5 of the output component 8 can be adjusted by adjusting the rotation speed N1 of the first driving member. In the process of accelerating or decelerating the rotation speed N5 of the output component 8, 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 rotation 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 effects.

[0062] 3. Maximum speed condition

[0063] See also Fig. 9 and Fig.10, the rotational speed N1 of the first driving member is in the positive direction, and the rotational speed N2 of the second driving member is in the positive direction. When the rotational speed N1 of the first driving member and the rotational speed N2 of the second driving member both reach the maximum rotational speed, the rotational speed N5 of the output member 8 also reaches the maximum rotational speed, and the vehicle speed reaches the maximum vehicle speed at this time. If the maximum rotational speeds of the rotational speed N1 of the first driving member and the rotational speed N2 of the second driving member are the same, then the maximum rotational speed that the rotational speed N5 of the output member 8 can reach is also the same as the maximum rotational speeds N1 and N2 of the first driving member and the second driving member, 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 rotation speed N1 of the first driving member is in the reverse direction and the rotation speed N2 of the second driving member is in the forward direction, when the vehicle is running at the starting stage or the medium and low speed stage, if the rotation speed control of the first driving member and the second driving member is inaccurate or the control fails, the ratio of the rotation speed N2 of the second driving member to the rotation speed N1 of the first driving member is less than [Z1×(Z3+Z4)] / (Z2×Z3), as Figure 7 As shown, the rotation speed N5 of the output component 8 may turn in the reverse direction, and the vehicle may suddenly reverse, which may easily cause a serious accident. In order to prevent this from happening, a one-way stopper 4 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 rotation speed N4 of the first planetary carrier 102, the second ring gear 203 and the third ring gear 303 to only turn in the forward direction and not in the reverse direction. In this way, it is ensured that the rotation speed N5 of the output component 8 always turns in the forward direction. Therefore, when this dangerous working condition occurs, since the one-way stopper 4 limits 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, the two driving members will drag each other at this time, and the ratio of the rotational speed N2 of the second driving member to the rotational speed N1 of the first driving member will always be equal to [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 equal to 0, and the rotational speed N5 of the output component 8 can only be 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 speed N1 of the first driving member turns to the forward direction, and the speed N2 of the second driving member turns to the reverse direction. The two driving members start to accelerate at the same time, and the ratio of the speed N2 of the second driving member to the speed N1 of the first driving member 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 8 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 driving member to the rotation speed N1 of the first driving member is less than [Z1×(Z3+Z4)] / (Z2×Z3), the rotation speed N5 of the output component 8 may turn to the forward direction, and 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 4 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 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, so as to ensure that the rotation speed N5 of the output component 8 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 speed of the second driving member is N2, the direction of rotation is positive, and the 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 4 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 8 rotates forward. The power of the second driving member is output through the second planetary gear 2 and the third planetary gear 3 to reduce speed and increase torque. The transmission ratio is [(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 of rotation 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 4 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 8 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 dual-drive three-planet gear continuously variable transmission mechanism and the speed change method thereof provided by the embodiment of the present invention have the following advantages:

[0073] 1. The dual-drive three-planet gear continuously variable transmission mechanism of 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 dual-drive three-planetary gear continuously variable transmission mechanism of 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 dual-drive three-planetary gear continuously variable transmission mechanism of the embodiment of the present invention can realize stepless and continuous change of the output speed. The input end drive component can work in the high-efficiency range for a long time, which improves the working efficiency, can achieve more economical effect in the use of energy, and can make more contributions to energy saving.

[0076] 4. The dual-drive three-planetary gear continuously variable transmission mechanism of 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 drive member and the second drive member to achieve stepless and continuous changes in 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 to a certain extent ensuring the promotion and popularity of this product.

[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 dual-drive three-planetary gear continuously variable transmission mechanism of 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 component. Compared with a high-power battery, a low-power battery can better prevent the occurrence of battery overheating. The embodiment of the present invention indirectly improves the safety of battery use.

[0080] 8. The dual-drive three-planetary gear continuously variable transmission mechanism of the embodiment of the present invention adopts a three-planetary 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] 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 dual-drive three-planet gear continuously variable transmission mechanism, characterized in that: The invention comprises a first planetary gear (1), a second planetary gear (2) and a third planetary gear (3), wherein a first ring gear (103) on the first planetary gear (1) is connected to a second planetary gear carrier (202) on the second planetary gear (2), the second planetary gear carrier (202) is connected to a third sun gear (301) on the third planetary gear (3) via a connecting shaft (7), the first planetary gear carrier (102) on the first planetary gear (1) is connected to the second ring gear (203) on the second planetary gear (2) and the third ring gear (303) on the third planetary gear (3), and the first planetary gear carrier (102) is connected to the second ring gear (203) on the second planetary gear (2) and the third ring gear (303) on the third planetary gear (3). A one-way stopper (4) is provided on the connecting body of the planet carrier (102), the second gear ring (203) and the third gear ring (303); the third planet carrier (302) on the third planetary gear row (3) is connected to an output component (8); the first sun gear (101) on the first planetary gear row (1) is connected to a first driving member via a first input shaft (5); the second input shaft (6) connected to the second sun gear (201) on the second planetary gear row (2) passes through the first sun gear (101), the first input shaft (5) and the first driving member to be connected to the second driving member; 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 (4) is used to limit the rotation direction of the first planetary carrier (102), the second ring gear (203) and the third ring gear (303). The one-way stopper (4) makes the rotation direction of the first planetary carrier (102), the second ring gear (203) and the third ring gear (303) only consistent with the rotation direction of the second driving member.

2. A speed changing method based on the dual-drive three-planetary gear continuously variable transmission mechanism according to claim 1, characterized in that: The first driving member and the first sun gear (101) are connected via a first input shaft (5), 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 (6), so that the rotation speed of the second driving member is the same as the rotation speed of the second sun gear (201); the first planet carrier (102), the second ring gear (203) and the third ring gear (303) are connected, so that the rotation speeds of the first planet carrier (102), the second ring gear (203) and the third ring gear (303) are the same. The first ring gear (103), the second planetary carrier (202) and the third sun gear (301) are connected so that the rotation speeds of the first ring gear (103), the second planetary carrier (202) and the third sun gear (301) are the same; the output component (8) is connected to the third planetary carrier (302) so that the rotation speeds of the third planetary carrier (302) and the output component (8) are the same; by adjusting and controlling the rotation speeds of the first driving component and the second driving component, the rotation speed of the output component (8) is continuously changed, and in this process, the speed ratio will also change accordingly.

3. The speed changing method of the dual-drive three-planetary gear continuously variable transmission mechanism according to claim 2, characterized in that: The rotation speed of the first driving member and the rotation speed of the first sun gear (101) are set to N1, the rotation speed of the second driving member and the rotation speed of the second sun gear (201) are set to N2, the rotation speed of the first ring gear (103), the second planet carrier (202) and the third sun gear (301) are set to N3, the rotation speed of the first planet carrier (102), the second ring gear (203) and the third ring gear (303) are set to N4, the rotation speed of the third planet carrier (302) and the output member (8) are set to 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 The number of teeth is Z3, 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 adjusting and controlling the rotational speed N1 of the first driving member and the rotational speed N2 of the second driving member, the rotational speed N5 of the output component (8) can be continuously and steplessly changed; 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 state of the output component (8) includes state A, state B, state C, state D and state E.

4. The speed changing method of the dual-drive three-planetary gear continuously variable transmission mechanism according to claim 3, characterized in that: In the state A, the rotational speed N1 of the first driving member is in the reverse direction, the rotational speed N2 of the second driving member is in the forward direction, the ratio of the rotational speed N2 of the second driving member to the rotational speed N1 of the first driving member is equal to [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 0, and the rotational speed N5 of the output component (8) is in the forward direction.

5. The speed changing method of the dual-drive three-planetary gear continuously variable transmission mechanism according to claim 3, characterized in that: In the state B, the rotational speed N1 of the first driving member turns in the reverse direction, the rotational speed N2 of the second driving member turns in the forward direction, the ratio of the rotational speed N2 of the second driving member to the rotational speed N1 of the first driving member 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) turns in the forward direction, and the rotational speed N5 of the output component (8) turns in the forward direction.

6. The speed changing method of the dual-drive three-planetary gear continuously variable transmission mechanism according to claim 3, characterized in that: In the state C, the rotational speed N1 of the first driving member is in the reverse direction, the rotational speed N2 of the second driving member is in the forward direction, the ratio of the rotational speed N2 of the second driving member to the rotational speed N1 of the first driving member is less than [Z1×(Z3+Z4)] / (Z2×Z3), the rotational speed N4 of the first planetary carrier (102), the second gear ring (203) and the third gear ring (303) is in the reverse direction, and the rotational speed N5 of the output component (8) is in the forward direction or the reverse direction. In order to prevent this from happening, a one-way stopper (4) is provided on the connecting body of the first planetary carrier (102), the second gear ring (203) and the third gear ring (303), so as to limit the rotational speed N4 of the first planetary carrier (102), the second gear ring (203) and the third gear ring (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 (8) is always in the forward direction.

7. The speed changing method of the dual-drive three-planetary gear continuously variable transmission mechanism according to claim 3, characterized in that: In the state D, the rotational speed N1 of the first driving member is 0, the rotational speed N2 of the second driving member is in the positive direction, the rotational speed N4 of the first planetary carrier (102), the second ring gear (203) and the third ring gear (303) are in the positive direction, and the rotational speed N5 of the output component (8) is in the positive direction.

8. The speed changing method of the dual-drive three-planetary gear continuously variable transmission mechanism according to claim 3, characterized in that: In the state E, the rotational speed N1 of the first driving member and the rotational speed N2 of the second driving member are the same in magnitude and both are in the positive direction; the rotational speed N4 of the first planetary 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 both are in the positive direction; the rotational speed N5 of the output component (8) is the same in magnitude as the N1, N2 and N4 and both are in the positive direction; and the transmission ratio of the state E is 1.

9. The speed changing method of the dual-drive three-planetary gear continuously variable transmission mechanism according to claim 3, characterized in that: When the first driving member fails, the rotation speed of the second driving member is N2, the direction of rotation is positive, and the rotation speed N4 of the first planetary carrier (102), the second gear ring (203) and the third gear ring (303) has a reverse trend. At this time, the one-way stopper (4) limits their reverse rotation, so that the rotation speed N4 of the first planetary carrier (102), the second gear ring (203) and the third gear ring (303) is 0, and the rotation speed N5 of the output component (8) rotates in the positive direction. The power of the second driving member is output through the second planetary gear (2) and the third planetary gear (3) to reduce speed and increase torque, and the transmission ratio is [(Z3+Z4)×(Z5+Z6)] / (Z3×Z5).

10. The speed changing method of the dual-drive three-planetary gear continuously variable transmission mechanism according to claim 3, characterized in that: When the second driving member fails, the rotation speed of the first driving member is N1, and the direction is reverse. The rotation speed N4 of the first planetary carrier (102), the second gear ring (203) and the third gear ring (303) has a reverse trend. At this time, the one-way stopper (4) limits their reverse rotation, so that the rotation speed N4 of the first planetary carrier (102), the second gear ring (203) and the third gear ring (303) is 0, and the rotation speed N5 of the output component (8) 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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