Continuously variable transmission mechanism and its transmission method

Abstract

The application discloses a kind of stepless speed change mechanism, belongs to stepless speed changer technical field, including first planetary row, second planetary row and third planetary row, first gear ring on first planetary row is connected with second planet carrier on second planetary row, second planet carrier on second planetary row is connected with third sun gear on third planetary row by connecting shaft, first planet carrier on first planetary row is connected with second gear ring on second planetary row and third gear ring on third planetary row, and one-way stopper is arranged on the connecting body of first planet carrier, second gear ring and third gear ring.The application further discloses the speed change method of the stepless speed change mechanism.The connecting end of first driving member and second driving member of the stepless speed change mechanism of the application is respectively arranged at both ends, so that the input mode of two input ends is split-end input, the probability that two input ends will influence each other during operation is reduced, and the overall failure rate is further reduced.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of continuously variable transmission, in particular to a continuously variable transmission mechanism and a transmission method thereof. BACKGROUND

[0002] With the increasing demand for environmental protection, electric vehicle technology has become the mainstream research direction of major car companies. At present, electric vehicles mostly use fixed speed ratio reducers. Although a reducer with a large speed ratio can meet the power demand of the vehicle when starting and climbing, the large speed ratio limits the vehicle from reaching a high maximum speed, which 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 balance the maximum speed and climbing ability of the vehicle, many car companies have begun to install AMT transmission on electric vehicles. However, AMT transmission is a type of gear transmission by nature, which has the problems of gear jerk and power interruption. The transmission ratio range of AMT transmission is limited by the gear setting. When applied to heavy vehicles, a large number of gears need to be set in order to expand the transmission ratio range. The gear shifting process is slow and the operation is complex, which makes many heavy vehicle drivers reluctant to step on the brake. The gear shifting process of AMT transmission relies on a complex control strategy, and it is difficult to grasp the accurate gear shifting time, resulting in high energy consumption and low efficiency. The structure of AMT transmission is complex, the manufacturing cost is high, and the maintenance is difficult. SUMMARY

[0003] The present application aims to solve the above problems and provides a continuously variable transmission mechanism and a transmission method thereof.

[0004] To achieve the above-mentioned purpose, the present application provides a continuously variable transmission mechanism, which comprises a first planetary gear set, a second planetary gear set and a third planetary gear set. A first ring gear on the first planetary gear set is connected with a second carrier on the second planetary gear set. The second carrier is connected with a third sun gear on the third planetary gear set through a connecting shaft. A first carrier on the first planetary gear set is connected with a second ring gear on the second planetary gear set and a third ring gear on the third planetary gear set. A one-way stopper is arranged on the connecting body of the first carrier, the second ring gear and the third ring gear. A third carrier on the third planetary gear set is connected with an output component. A first sun gear on the first planetary gear set is connected with a first driving member through a first input shaft. A second input shaft connected with a second sun gear on the second planetary gear set passes through the second carrier, the connecting shaft, the third sun gear, the third carrier and the output component and is connected with a second driving member.

[0005] As a further description of the present application, the outer teeth of the first sun gear are engaged with a first planetary gear, the first planetary gear is installed on the first carrier, and the first planetary gear is engaged with the inner ring teeth of the first ring gear.

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

[0007] The outer teeth of the third sun gear mesh with third planetary gears, the third planetary gears are mounted on the third carrier, and the third planetary gears mesh with the inner ring teeth of the third ring gear.

[0008] As a further description of the present application, the one-way stopper is used to limit the rotation direction of the first carrier, the second ring gear and the third ring gear, and the one-way stopper makes the rotation direction of the first carrier, the second ring gear and the third ring gear consistent with the rotation direction of the second driving member.

[0009] The present application also provides a speed change method based on the stepless speed change mechanism, the first driving member and the first sun gear are connected through the first input shaft, so that the rotation speed of the first driving member is the same as that of the first sun gear; the second driving member and the second sun gear are connected through the second input shaft, so that the rotation speed of the second driving member is the same as that of the second sun gear; the first carrier, the second ring gear and the third ring gear are connected, so that the rotation speed of the first carrier, the second ring gear and the third ring gear is the same; the first ring gear, the second carrier and the third sun gear are connected, so that the rotation speed of the first ring gear, the second carrier and the third sun gear is the same; the output member is connected with the third carrier, so that the rotation speed of the third carrier and the output member is the same; the rotation speed of the output member is continuously changed steplessly by adjusting and controlling the rotation speed of the first driving member and the rotation speed of the second driving member, and in this process, the speed ratio also changes accordingly.

[0010] As a further illustration of the application, it is provided that the rotational speed of the first driving member and the first sun gear is N1, the rotational speed of the second driving member and the second sun gear is N2, the rotational speed of the first ring gear, the second carrier and the third sun gear is N3, the rotational speed of the first carrier, the second ring gear and the third ring gear is N4, the rotational speed of the third carrier and the output component 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 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 by the proportional relationship of the line segments in the vector diagram; by adjusting and controlling the rotational speed N1 of the first driving member and the rotational speed N2 of the second driving member, continuous stepless variation of the rotational speed N5 of the output component can be realized; 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 includes state A, state B, state C, state D and state E.

[0011] As a further illustration of the application, in the state A, the rotational direction of the rotational speed N1 of the first driving member is reverse, the rotational direction 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 carrier, the second ring gear and the third ring gear is 0, and the rotational direction of the rotational speed N5 of the output component is forward.

[0012] As a further illustration of the application, in the state B, the rotational direction of the rotational speed N1 of the first driving member is reverse, the rotational direction 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 greater than [Z1×(Z3+Z4)] / (Z2×Z3), the rotational direction of the rotational speed N4 of the first carrier, the second ring gear and the third ring gear is forward, and the rotational direction of the rotational speed N5 of the output component is forward.

[0013] As a further illustration of the application, in the state C, the rotation direction of the first driving member N1 is reversed, the rotation direction of the second driving member N2 is positive, the ratio of the rotation speed N2 of the second driving member and the rotation speed N1 of the first driving member is less than [Z1 x (Z3+Z4)] / (Z2 x Z3), the rotation direction of the first planetary carrier, the second ring gear and the third ring gear N4 is reversed, the rotation direction of the output member N5 can be positive or reversed, in order to prevent this from happening, 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 rotation direction of the first planetary carrier, the second ring gear and the third ring gear N4 is limited to be positive only, not reversed, so as to ensure that the rotation direction of the output member N5 is always positive.

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

[0015] As a further illustration of the application, in the state E, the rotation speed N1 of the first driving member and the rotation speed N2 of the second driving member are the same in size and positive in direction, the rotation speed N4 of the first planetary carrier, the second ring gear and the third ring gear is the same in size as N1 and N2 and positive in direction, and the rotation speed N5 of the output member is the same in size as N1, N2 and N4 and positive in direction, the transmission ratio of the state E is 1.

[0016] As a further illustration of the application, when the first driving member fails, the rotation speed of the second driving member N2 is positive, 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 its reverse rotation, so that the rotation speed N4 of the first planetary carrier, the second ring gear and the third ring gear is 0, the output member N5 rotates positively, the power of the second driving member is transmitted through the second planetary set and the third planetary set to increase the torque and output, and the transmission ratio is [(Z3+Z4) x (Z5+Z6)] / (Z3 x Z5).

[0017] As a further illustration of the present application, when the second driving member fails, the rotation speed of the first driving member is N1, the direction is reverse, the rotation speed N4 of the first planetary carrier, the second ring gear and the third ring gear has a tendency of reverse rotation, at this time the one-way stopper limits its reverse rotation, so that the rotation speed N4 of the first planetary carrier, the second ring gear and the third ring gear is 0, the rotation speed N5 of the output component is forward rotation, the power of the first driving member is output through the first planetary set and the third planetary set with deceleration and torque increase, and the transmission ratio is [(Z3+Z4)×(Z5+Z6)] / (Z3×Z5).

[0018] The continuously variable transmission mechanism and the transmission method thereof provided by the present application change the transmission ratio between the input end and the output end by adjusting the rotation speed of the first driving member and the second driving member and by the cooperation between the first planetary set, the second planetary set, the third planetary set and the one-way stopper, so that the continuously variable transmission of the output end is realized. The mechanism has the advantages of high transmission efficiency, large output torque, no power interruption, simple and reliable structure, low manufacturing cost, easy maintenance, simple and convenient speed regulation, etc. In addition, the connection ends of the first driving member and the second driving member of the continuously variable transmission mechanism are respectively arranged at the two ends thereof, so that the input mode of the two input ends is split-end input, the probability that the two input ends affect each other during operation is reduced, and the overall failure rate is further reduced. BRIEF DESCRIPTION OF DRAWINGS

[0019] Figure 1 is a schematic diagram of the continuously variable transmission mechanism provided by the embodiment of the present application;

[0020] Figure 2 is a rotation speed vector diagram of the first planetary set provided by the embodiment of the present application;

[0021] Figure 3 is a rotation speed vector diagram of the second planetary set provided by the embodiment of the present application;

[0022] Figure 4 is a rotation speed vector diagram of the third planetary set provided by the embodiment of the present application;

[0023] Figure 5 is a rotation speed vector diagram of the first planetary carrier, the second ring gear and the third ring gear provided by the embodiment of the present application; Figure 2 , Figure 3 , Figure 4 is a combined rotation speed vector diagram provided by the embodiment of the present application;

[0024] Figure 6 is a rotation speed vector diagram of the first planetary carrier, the second ring gear and the third ring gear when the rotation speed N4 is 0;

[0025] Figure 7 is a rotation speed vector diagram of the first planetary carrier, the second ring gear and the third ring gear when the rotation speed N4 is less than 0;

[0026] Figure 8 is a rotational speed vector diagram when the rotational speed N1 of the first driving member is 0 according to an embodiment of the present application;

[0027] Figure 9 is a rotational speed vector diagram when the rotational speeds of the first driving member and the second driving member are the same according to an embodiment of the present application;

[0028] Figure 10 is a rotational speed vector diagram when the rotational directions of the rotational speeds N1 and N2 of the first driving member and the second driving member are both positive according to an embodiment of the present application;

[0029] Figure 11 is a rotational speed vector diagram when the rotational speed N4 of the first carrier, the second ring gear and the third ring gear is 0 in a reverse driving condition according to an embodiment of the present application;

[0030] Figure 12 is a rotational speed vector diagram when the rotational speed N4 of the first carrier, the second ring gear and the third ring gear is less than 0 in a reverse driving condition according to an embodiment of the present application;

[0031] Figure 13 is a rotational speed vector diagram when the first driving member fails and the rotational direction of the rotational speed N2 of the second driving member is positive according to an embodiment of the present application;

[0032] Figure 14 is a rotational speed vector diagram when the second driving member fails and the rotational direction of the rotational speed N1 of the first driving member is negative according to an embodiment of the present application.

[0033] Reference signs:

[0034] 1 - first planetary gear set, 101 - first sun gear, 102 - first carrier, 103 - first ring gear, 2 - second planetary gear set, 201 - second sun gear, 202 - second carrier, 203 - second ring gear, 3 - third planetary gear set, 301 - third sun gear, 302 - third carrier, 303 - third ring gear, 4 - one-way clutch, 5 - first input shaft, 6 - second input shaft, 7 - connecting shaft, 8 - output component. DETAILED DESCRIPTION

[0035] First we have to explain the purpose of our invention, we are to solve the AMT transmission shift jerk, power interruption problems; AMT transmission ratio range is subject to gear settings, applied in heavy vehicles, in order to expand the range of transmission ratio, need to set a very large gear, slow shift process, complex operation, resulting in many truck drivers do not want to step on the brake; AMT transmission shift process depends on complex control strategy, it is difficult to grasp the accurate shift timing, high energy consumption, low efficiency problems; AMT transmission structure is complex, high manufacturing cost, maintenance difficulties and other existing problems, so a kind of continuously variable transmission mechanism to solve the existing problems.

[0036] The embodiments of the present application will be described in detail below with reference to the drawings. First, we will introduce the specific structure of the embodiments of the present application.

[0037] Referring to Figure 1 A continuously variable transmission mechanism, comprising a first planetary gear set 1, a second planetary gear set 2 and a third planetary gear set 3, the first ring gear 103 on the first planetary gear set 1 is connected with the second carrier 202 on the second planetary gear set 2, the second carrier 202 on the second planetary gear set 2 is connected with the third sun gear 301 on the third planetary gear set 3 through the connecting shaft 7, the first carrier 102 on the first planetary gear set 1 is connected with the second ring gear 203 on the second planetary gear set 2 and the third ring gear 303 on the third planetary gear set 3, the connecting body of the first carrier 102, the second ring gear 203 and the third ring gear 303 is provided with a one-way stopper 4, the third carrier 302 on the third planetary gear set 3 is connected with an output component 8, the first sun gear 101 on the first planetary gear set 1 is connected with a first driving member through a first input shaft 5, the second sun gear 201 on the second planetary gear set 2 is connected with a second input shaft 6 which passes through the second carrier 202, the connecting shaft 7, the third sun gear 301, the third carrier 302 and the output component 8 and is connected with a second driving member.

[0038] Referring to Figure 1 The outer teeth of the first sun gear 101 are engaged with the first planetary gear, the first planetary gear is installed on the first carrier 102, and the first planetary gear is engaged with the inner teeth of the first ring gear 103; the outer teeth of the second sun gear 201 are engaged with the second planetary gear, the second planetary gear is installed on the second carrier 202, and the second planetary gear is engaged with the inner teeth of the second ring gear 203; the outer teeth of the third sun gear 301 are engaged with the third planetary gear, the third planetary gear is installed on the third carrier 302, and the third planetary gear is engaged with the inner teeth of the third ring gear 303.

[0039] Referring to Figure 1The 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, and the rotation direction of the first planetary carrier 102, the second ring gear 203 and the third ring gear 303 is consistent with the rotation direction of the second driving member only.

[0040] Now we need to combine the specific structure of the embodiment of the application to explain a variable speed method based on a continuously variable transmission mechanism.

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

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

[0043] Therefore, the rotation speed of the first driving member and the first sun gear 101 is the same, which is set as N1; the rotation speed of the second driving member and the second sun gear 201 is the same, which is set as N2; the rotation speed of the first ring gear 103, the second planetary carrier 202 and the third sun gear 301 is the same, which is set as N3; the rotation speed of the first planetary carrier 102, the second ring gear 203 and the third ring gear 303 is the same, which is set as N4; the rotation speed of the third planetary carrier 302 and the output component 8 is the same, which is set as N5; the number of teeth of the first sun gear 101 is set as Z1, the number of teeth of the first ring gear 103 is set as Z2, the number of teeth of the second sun gear 201 is set as Z3, the number of teeth of the second ring gear 203 is set as Z4, the number of teeth of the third sun gear 301 is set as Z5, and the number of teeth of the third ring gear 303 is set as Z6.

[0044] According to the rotation speed vector calculation method of planetary gears, the rotation speed vector diagram of the first planetary row 1 is obtained, as shown in Figure 2 N1 is the rotation speed of the first sun gear 101, N3 is the rotation speed of the first ring gear 103, and N4 is the rotation speed of the first planetary carrier 102. The length of N1, N3 and N4 represents the rotation speed, the arrow direction represents the rotation direction, the arrow upward represents the positive rotation speed, and the arrow downward represents the negative rotation speed. It is set that L2 / L3=Z1 / Z2.

[0045] According to the rotation speed vector calculation method of planetary gears, the rotation speed vector diagram of the second planetary row 2 is obtained, as shown in Figure 3 N2 is the rotation speed of the second sun gear 201, N4 is the rotation speed of the second ring gear 203, and N3 is the rotation speed of the second planetary carrier 202. The length of N2, N3 and N4 represents the rotation speed, the arrow direction represents the rotation direction, the arrow upward represents the positive rotation speed, and the arrow downward represents the negative rotation speed. It is set that L2 / L1=Z3 / Z4.

[0046] According to the planetary gear speed vector calculation method, the speed vector diagram of the third planetary gear 3 is obtained, as shown in the figure: Figure 4 As shown in the figure, 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 arrows indicate the direction of the speeds. An upward arrow indicates forward speed, and a downward arrow indicates 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, 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 of N1, N2, N3, N4, and N5 are determined, the remaining three values ​​can be calculated using the proportional relationship of the line segments in the vector diagram. That is, if the rotational speed N1 of the first driving member and the rotational speed N2 of the second driving member are determined, the rotational speed N5 of the output member 8 is also uniquely determined. By adjusting and controlling the rotational speeds N1 and N2 of the first and second driving members, the rotational speed N5 of the output member 8 can be continuously and steplessly varied.

[0050] The speed change principle of the 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 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. The two driving members start to accelerate at the same time, and 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 (such as Figure 5 ) or equal to (such as Figure 6), the rotational speed N5 of the output member 8 can be gradually accelerated from 0 and turned to positive. In this case, the transmission ratio is maximum, the power of the first driving member and the second driving member is coupled together, the speed is reduced and the torque is increased, so that the vehicle is accelerated and moves forward.

[0053] 2. Acceleration and deceleration

[0054] The acceleration and deceleration process can be divided into three cases according to the turning direction of the rotational speed N1 of the first driving member, and specifically includes:

[0055] 1) Case one

[0056] Referring to Figure 5 and Figure 6 , the rotational speed N1 of the first driving member is in reverse direction, and the rotational speed N2 of the second driving member is in 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 always greater than or equal to [Z1×(Z3+Z4)] / (Z2×Z3). By controlling the increasing and decreasing speed of 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 member 8 can be gradually increased or decreased and turned to forward direction, so that the vehicle is accelerated or decelerated and moves forward.

[0057] 2) Case two

[0058] Referring to Figure 8 , the rotational speed N1 of the first driving member is gradually reduced to 0, and the rotational speed N2 of the second driving member is turned to forward direction. By controlling the increasing and decreasing speed of 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 member 8 can be gradually increased or decreased and turned to forward direction, so that the vehicle is accelerated or decelerated and moves forward.

[0059] 3) Case three

[0060] Referring to Figure 10 , the rotational speed N1 of the first driving member is in forward direction, and the rotational speed N2 of the second driving member is in forward direction. By controlling the increasing and decreasing speed of 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 member 8 can be gradually increased or decreased and turned to forward direction, so that the vehicle is accelerated or decelerated and moves forward.

[0061] In addition, the acceleration and deceleration speed regulation method can also be to maintain the rotation speed N1 of the first driving member unchanged, to regulate the rotation speed N5 of the output member 8 by regulating the size of the rotation speed N2 of the second driving member; or to maintain the rotation speed N2 of the second driving member unchanged, to regulate the rotation speed N5 of the output member 8 by regulating the size of the rotation speed N1 of the first driving member. In the process of realizing the acceleration or deceleration of the rotation speed N5 of the output member 8, the first driving member and the second driving member can be controlled according to the respective high-efficiency working zones, and the control system controls the acceleration, deceleration and maintaining rotation speed of the first driving member and the second driving member according to the current working condition. In this way, the first driving member and the second driving member can work in the respective high-efficiency working zones for a long time, so as to realize the energy-saving effect.

[0062] 3. Maximum vehicle speed working condition

[0063] Referring to Figure 9 and Figure 10 , the rotation direction of the rotation speed N1 of the first driving member is forward, and the rotation direction of the rotation speed N2 of the second driving member is forward. When the rotation speed N1 of the first driving member and the rotation speed N2 of the second driving member both reach the maximum rotation speed, the rotation speed N5 of the output member 8 also reaches the maximum rotation speed, at which time the vehicle speed reaches the maximum vehicle speed. If the maximum rotation speeds of the rotation speed N1 of the first driving member and the rotation speed N2 of the second driving member are the same, then the maximum rotation speed that can be reached by the rotation speed N5 of the output member 8 is also the same as the maximum rotation speeds N1 and N2 of the first driving member and the second driving member, at which time the transmission ratio is 1.

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

[0065] Example: Referring to Figure 7 , when the rotation direction of the rotation speed N1 of the first driving member is reverse, and the rotation direction of the rotation speed N2 of the second driving member is forward, the vehicle is running in the starting stage or the low-speed stage, if the rotation speed control of the first driving member and the second driving member is inaccurate or 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), such as Figure 7As shown, the reverse direction of the rotation speed N5 of the output component 8 can appear to be reversed, at which time the vehicle suddenly appears to be moving in reverse, and serious accidents are extremely likely to occur. In order to prevent this from happening, by setting the one-way stopper 4 on the connecting body of the first planetary carrier 102, the second ring gear 203, and the third ring gear 303, the rotation direction of the rotation speed N4 of the first planetary carrier 102, the second ring gear 203, and the third ring gear 303 is limited to be positive, and cannot be reversed. In this way, the rotation direction of the rotation speed N5 of the output component 8 is always positive. Therefore, when the dangerous working condition occurs, since the one-way stopper 4 limits the rotation direction of the rotation speed N4 of the first planetary carrier 102, the second ring gear 203, and the third ring gear 303 to be positive, and cannot be reversed, at this time, the two driving components will drag each other, the ratio of the rotation speed N2 of the second driving component to the rotation speed N1 of the first driving component 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 direction of the rotation speed N5 of the output component 8 can only be positive, so the situation of suddenly moving in reverse will not occur.

[0066] 4. Reverse working condition

[0067] Referring to Figure 11 and Figure 12 , when reversing, the rotation direction of the rotation speed N1 of the first driving component is positive, and the rotation direction of the rotation speed N2 of the second driving component is reversed. The two driving components are simultaneously started and accelerated, and by controlling the ratio of the rotation speed N2 of the second driving component to the rotation speed N1 of the first driving component to always be greater than (such as Figure 12 ) or equal to (such as Figure 11 ) [Z1×(Z3+Z4)] / (Z2×Z3), the rotation speed N5 of the output component 8 can be gradually accelerated from 0 and the rotation direction is reversed. If the rotation speed control of the first driving component and the second driving component is not accurate or control fails, and the ratio of the rotation speed N2 of the second driving component to the rotation speed N1 of the first driving component is less than [Z1×(Z3+Z4)] / (Z2×Z3), the rotation direction of the rotation speed N5 of the output component 8 can appear to be positive, at which time the vehicle suddenly appears to be moving forward, and serious accidents are extremely likely to occur. In order to prevent this from happening, by setting the one-way stopper 4 on the connecting body of the first planetary carrier 102, the second ring gear 203, and the third ring gear 303, the rotation direction of the rotation speed N4 of the first planetary carrier 102, the second ring gear 203, and the third ring gear 303 is limited to be reversed, and cannot be positive, in this way, the rotation direction of the rotation speed N5 of the output component 8 is always reversed.

[0068] In addition to the normal working condition and the dangerous working condition described above, there are some emergency working conditions that need to be dealt with, and the embodiments of the present application have considered and solved them.

[0069] Example: Referring to Figure 13When the first driving member fails, the rotation speed of the second driving member is N2, the rotation direction is positive, the rotation speed N4 of the first planet 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 rotation speed N4 of the first planet carrier 102, the second ring gear 203 and the third ring gear 303 is 0, the rotation speed N5 of the output component 8 is positive rotation, the power of the second driving member is output through the second planetary gear set 2 and the third planetary gear set 3, the transmission ratio is [(Z3+Z4) x (Z5+Z6)] / (Z3 x Z5), so that the vehicle can continue to accelerate or decelerate forward.

[0070] Referring to Figure 14 When the second driving member fails, the rotation speed of the first driving member is N1, the rotation direction is reverse, the rotation speed N4 of the first planet 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 rotation speed N4 of the first planet carrier 102, the second ring gear 203 and the third ring gear 303 is 0, the rotation speed N5 of the output component 8 is positive rotation, the power of the first driving member is output through the first planetary gear set 1 and the third planetary gear set 3, the transmission ratio is [Z2 x (Z5+Z6)] / (Z1 x Z5), so that the vehicle can continue to accelerate or decelerate forward.

[0071] Therefore, when one driving member fails, the other driving member can still drive the vehicle to run, although the power is reduced, but one driving member can drive the vehicle to run to a maintenance site or a safe place, so that the reliability of the vehicle can be greatly improved.

[0072] The stepless speed change mechanism and the speed change method provided by the embodiment of the application have the following advantages:

[0073] 1. In the stepless speed change mechanism, the speed regulation process is uninterrupted, and the operation is quiet and stable, so that the user has a better driving experience, and the customer demand can be greatly met in the sense, thereby laying a very good foundation for the promotion and use of the product.

[0074] 2. The stepless speed change mechanism can realize large torque at the output end from low speed to high speed, so that the vehicle has the ability of rapid acceleration start during driving, and the large torque can climb a larger slope during climbing, and the large torque can meet the driving needs of more people, so that the audience of the product is larger.

[0075] 3. The stepless speed change mechanism can realize stepless and continuous change of the output rotation speed, the input end driving member can work in the high efficiency interval for a long time, the work efficiency is improved, the use of energy can be more saved, and more contributions can be made in energy saving.

[0076] 4、The stepless speed change mechanism of the embodiment of the present application has simple and convenient speed adjustment, and only the rotation speeds of the first driving member and the second driving member need to be controlled to realize stepless and continuous change of the output rotation speed, thereby reducing the requirement of the vehicle on the control system, making the application range of the product wider, and ensuring the popularization and popularity of the product to a certain extent.

[0077] 5、The power of the first driving member and the second driving member of the embodiment of the present application is coupled together to drive the vehicle to run, when one of the driving members fails, the other driving member can still continue to drive the vehicle to run, thereby ensuring that the vehicle owner can rely on the other driving member to drive the vehicle even if one driving member fails, and the vehicle owner can timely drive the vehicle to a repair site, avoiding the occurrence of the event of calling a tow truck, and better caring the vehicle experience of the vehicle owner.

[0078] 6、Compared with the driving mode of the traditional single driving member, the product of the embodiment of the present application can not only be driven by double driving members, but also can select driving members with smaller size and lower rotation speed to be matched, the small-size driving member is more conducive to the arrangement design of the driving member in the vehicle body, and is more convenient for the aesthetic design of the appearance of the vehicle body, and the use of smaller driving members can save costs.

[0079] 7、The stepless speed change mechanism of the embodiment of the present application has high transmission efficiency, under the same working condition, a motor with lower power and lower rotation speed can be selected as the driving member, compared with the high-power battery, the low-power battery can better prevent the occurrence of the battery overheating, and indirectly improves the use safety of the battery.

[0080] 8、The stepless speed change mechanism of the embodiment of the present application adopts three planetary gear sets to increase the transmission ratio, so that the torque is further increased, and can be applied to heavy trucks, dump trucks, passenger cars and other heavy vehicles, thereby further widening the application range of the embodiment of the present application.

[0081] 9、The connection ends of the first driving member and the second driving member of the stepless speed change mechanism of the embodiment of the present application are respectively arranged at the two ends thereof, so that the input modes of the two input ends are split-end input, the probability that the two input ends affect each other during operation is reduced, and the overall failure rate is reduced.

[0082] The above technical solution only reflects the preferred technical solution of the present application, and some changes made by the person skilled in the art to some parts of the present application also reflect the principle of the present application, and belong to the protection scope of the present application.

Claims

1. A speed changing method of a continuously variable transmission mechanism, characterized in that: The continuously variable transmission mechanism comprises a first planetary row (1), a second planetary row (2) and a third planetary row (3); the first ring gear (103) on the first planetary row (1) is connected to the second planetary carrier (202) on the second planetary row (2); the second planetary carrier (202) is connected to the third sun gear (301) on the third planetary row (3) via a connecting shaft (7); the first planetary carrier (102) on the first planetary row (1) is connected to the second ring gear (203) on the second planetary row (2) and the third ring gear (303) on the third planetary row (3); the first planetary carrier (102), the second planetary carrier (202) and the third sun gear (301) on the third planetary row (3) are connected; A one-way stopper (4) is provided on the connecting body of the second ring gear (203) and the third ring gear (303); the third planet carrier (302) on the third planetary row (3) is connected to an output component (8); the first sun gear (101) on the first planetary row (1) is connected to the first driving component via a first input shaft (5); the second input shaft (6) connected to the second sun gear (201) on the second planetary row (2) passes through the second planet carrier (202), the connecting shaft (7), the third sun gear (301), the third planet carrier (302) and the output component (8) to be connected to the second driving component; The first planetary gear is meshed with the outer teeth of the first sun gear (101), the first planetary gear is mounted on the first planet carrier (102), and the first planetary gear is meshed with the inner ring teeth 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 outer teeth of the third sun gear (301) are meshed with a third planetary gear, 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 ring gear (303); The one-way stopper (4) is used to limit the rotation direction of the first planet carrier (102), the second ring gear (203) and the third ring gear (303), and the one-way stopper (4) 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 driving member; The first driving member and the first sun gear (101) are connected via the first input shaft (5), so that the rotational speed of the first driving member is the same as the rotational speed of the first sun gear (101); the second driving member and the second sun gear (201) are connected via the second input shaft (6), so that the rotational speed of the second driving member is the same as the rotational 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 first planet carrier (102), the second ring gear (203) and the third ring gear (303) are connected. The first ring gear (103), the second planet carrier (202) and the third sun gear (301) are connected so that the first ring gear (103), the second planet carrier (202) and the third sun gear (301) have the same rotational speed; the output component (8) is connected to the third planet carrier (302) so that the third planet carrier (302) and the output component (8) 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 (8) is continuously changed, and in this process, the speed ratio also changes accordingly.

2. The speed changing method of a continuously variable transmission mechanism according to claim 1, 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 driving member and the rotational speed of the second sun gear (201) are N2, the rotational speed of the first ring gear (103), the second planetary carrier (202) and the third sun gear (301) are N3, the rotational speed of the first planetary carrier (102), the second ring gear (203) and the third ring gear (303) are N4, the rotational speed of the third planetary carrier (302) and the output member (8) 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 The number of teeth is Z3, the number of teeth of the second ring gear (203) is Z4, the number of teeth of the third sun gear (301) is Z5, and the number of teeth of the third ring gear (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 member (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 member (8) includes state A, state B, state C, state D and state E.

3. The speed changing method of a continuously variable transmission mechanism according to claim 2, characterized in that: In the state A, the rotational direction of the rotational speed N1 of the first driving member is reverse, the rotational direction 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 (102), the second ring gear (203) and the third ring gear (303) is 0, and the rotational direction of the rotational speed N5 of the output component (8) is forward.

4. The speed changing method of a continuously variable transmission mechanism according to claim 2, wherein: In the state B, 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 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 in the forward direction, and the rotational speed N5 of the output member (8) is in the forward direction.

5. The speed changing method of a continuously variable transmission mechanism according to claim 2, 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 ring gear (203) and the third ring gear (303) is in the reverse direction, and the rotational speed N5 of the output component (8) is in the forward or 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 ring gear (203) and the third ring gear (303), limiting 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 (8) is always in the forward direction.

6. The speed changing method of a continuously variable transmission mechanism according to claim 2, 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 member (8) is in the positive direction.

7. The speed changing method of a continuously variable transmission mechanism according to claim 2, 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 the directions of rotation are both positive; 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 the directions of rotation are both positive; the rotational speed N5 of the output component (8) is the same in magnitude as the N1, N2 and N4 and the directions of rotation are both positive; and the transmission ratio of the state E is 1.

8. The speed changing method of a continuously variable transmission mechanism according to claim 2, wherein: When the first driving member fails, the speed of the second driving member is N2, the direction of rotation is forward, 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 (4) limits their 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) with deceleration and torque increase, and the transmission ratio is [(Z3+Z4)×(Z5+Z6)] / (Z3×Z5).

9. The speed changing method of a continuously variable transmission mechanism according to claim 2, 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 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 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 (8) rotates in the forward direction. 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).

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