CN115899203A - Four planetary row continuously variable transmission mechanism with unilateral stepped transmission and its transmission method - Google Patents

Abstract

The invention discloses a four-planet row stepless speed change mechanism and a speed change method thereof for unilateral step-by-step transmission, which belong to the technical field of stepless transmissions and include a first planetary row, a second planetary row, a third planetary row and a fourth planetary row , the third sun gear on the third planetary row is connected to the transmission stage. The transmission stage includes transmission gear A and transmission gear B. Transmission gear A and transmission gear B are meshed through external teeth. The first ring gear on the first planetary row passes through the first A connection shaft is connected with the second sun gear on the second planet row, the second ring gear on the second planet row is connected with the third planet carrier on the third planet row, and the third planet carrier on the third planet row passes through The second connecting shaft is connected with the fourth sun gear on the fourth planet row, and the output component is connected on the fourth planet carrier. A transmission stage is added between the first planetary row and the first driving member of the four-planet row stepless transmission mechanism of the present invention, and the transmission ratio provided by the transmission stage widens the power selection range of the first driving member.

Description

Four planetary row continuously variable transmission mechanism with unilateral stepped transmission and its transmission method

technical field

The invention relates to the technical field of continuously variable transmissions, in particular to a four-planetary continuously variable transmission mechanism with unilateral stepped transmission and a transmission method thereof.

Background technique

As the society's requirements for environmental protection are getting higher and higher, electric vehicle technology has become the mainstream research direction of major car companies. At present, most electric vehicles use a fixed speed ratio reducer. Although a large speed ratio reducer can be used to meet the power demand when the vehicle starts to climb, but the large speed ratio limits the vehicle to a higher maximum speed. The reason why the maximum speed of electric vehicles is generally lower than that of fuel vehicles. In order to take into account the maximum speed and climbing ability of the vehicle, many car companies have begun to install AMT transmissions on electric vehicles, but AMT transmissions are step-shift transmissions in principle, and there are inherent problems of shifting frustration and power interruption; AMT transmissions The transmission ratio range is limited by the gear setting. It is applied to heavy-duty vehicles. In order to expand the transmission ratio range, it is necessary to set a lot of gears. The gearing process relies on complex control strategies, it is difficult to grasp the exact timing of gear shifting, and there are problems of high energy consumption and low efficiency; AMT transmissions have complex structures, high manufacturing costs, and difficult maintenance.

Contents of the invention

The object of the present invention is to solve the above-mentioned problems, and a four-planet row continuously variable transmission mechanism and a transmission method thereof have been designed with unilateral step-by-step transmission.

To achieve the above object, the technical solution of the present invention is a four-planet row continuously variable transmission mechanism with unilateral staged transmission, including a first planetary row, a second planetary row, a third planetary row and a fourth planetary row, the third planetary row The third sun gear on the row is connected to the transmission stage, the transmission stage includes transmission gear A and transmission gear B, the transmission gear A and the transmission gear B are meshed through external teeth, the first planetary gear on the first planetary row The ring gear is connected to the second sun gear on the second planet row through the first connection shaft, and the second ring gear on the second planet row is connected to the third planet carrier on the third planet row, so The third planetary carrier is connected to the fourth sun gear on the fourth planetary row through the second connecting shaft, the fourth planetary carrier on the fourth planetary row is connected to the output component, and the first planetary row The first planetary carrier on the second planetary row, the second planetary carrier on the second planetary row, the third ring gear on the third planetary row and the fourth ring gear on the fourth planetary row are all connected in the same speed connection On the body, a one-way stopper is arranged on the connecting body of the same speed, and the third sun gear passes through the third planetary carrier, the second connecting shaft, and the fourth sun gear sequentially through the transmission shaft. , the fourth planetary carrier and the output member are connected with the transmission gear A, the transmission gear B is connected with the second driving member through the second input shaft, and the first sun gear on the first planetary row is connected through The first input shaft sequentially passes through the first connecting shaft, the second sun gear, the third sun gear, the transmission shaft and the transmission gear A to be connected to the first driving member.

As a further description of the present invention, the first connecting shaft, the second sun gear, the third sun gear, the third planet carrier, the second connecting shaft, the fourth sun gear, the fourth planet carrier, the output member, the transmission shaft and The transmission gears A all pass through the hollow structure.

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

The present invention also provides a speed change method based on a four-planet row continuously variable transmission mechanism based on unilateral staged transmission. The rotational speeds of the first sun gear are the same; the second drive member and the third sun gear are connected through the second input shaft, the transmission stage, and the transmission shaft, so that the rotational speed of the second drive member is the same as that of the third sun gear. The rotational speed is proportional to the transmission ratio of the transmission stage; the first planetary carrier, the second planetary carrier, the third ring gear and the fourth ring gear are all connected to the connecting body with the same rotating speed, so that the first planetary carrier, The rotation speeds of the second planet carrier, the third ring gear and the fourth ring gear are the same; the first ring gear and the second sun gear are connected through a first connecting shaft, so that the rotation speed of the first ring gear and the The rotation speeds of the second sun gear are the same; the second ring gear is connected to the third planet carrier, and the third planet carrier is connected to the fourth sun gear through a second connecting shaft, so that the second ring gear, the The rotation speed of the third planetary carrier is the same as that of the fourth sun gear; the fourth planetary carrier is connected with the output component, so that the rotation speed of the fourth planetary carrier is the same as that of the output component.

As a further description 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 third sun gear is _N2 , and the transmission ratio of the transmission stage is i , the rotational speed of the second driving member is N ₂ ×i, the rotational speeds of the first planet carrier, the second planet carrier, the third ring gear and the fourth ring gear are N ₃ , the The speed of the first ring gear and the second sun gear is N ₄ , the speed of the second ring gear, the third planet carrier and the fourth sun gear is N ₅ , and the fourth planet The rotational speed of the frame and the output part is _N6 ; when any two values of _N1 , _N2 , _N3 , _N4 , _N5 , _N6 are determined, the other four values can be determined by the line segment in the vector diagram The proportional relationship is calculated; by driving the first driving member and the second driving member to adjust and control the rotational speed N ₁ of the first sun gear and the rotational speed N ₂ of the third sun gear, the The continuous stepless change of the rotation speed _N6 of the output member, wherein when the rotation speed _N3 of the first planet carrier, the second planet carrier, the third ring gear and the fourth ring gear is 0, the first The ratio of the rotational speed _N1 of the sun gear to the rotational speed _N2 of the third sun gear is P; the rotational speed _N1 of the first sun gear is adjusted and controlled by driving the first driving member and the second driving member and the rotational speed N ₂ of the third sun gear, so that the output states of the output member include state A, state B, state C, state D and state E.

As a further description of the present invention, in the state A, the rotation speed N ₃ of the first planet carrier, the second planet carrier, the third ring gear and the fourth ring gear is 0, and the The first driving member and the second driving member control the ratio of the rotational speed _N1 of the first sun gear to the rotational speed _N2 of the third sun gear to be P, and the steering direction is both positive, so that the output member The steering of the rotational speed _N6 is positive, and the transmission ratio is at the maximum value state at this time.

As a further description of the present invention, in the state B, the rotation speed _N3 of the first planetary carrier, the second planetary carrier, the third ring gear and the fourth ring gear is not 0, and the steering Forward direction, the first driving member and the second driving member control the ratio of the rotational speed N ₁ of the first sun gear to the rotational speed N ₂ of the third sun gear to be less than P, and the steering is both positive, Make the rotation speed _N6 of the output member positive.

As a further description of the present invention, in the state C, the rotation speed N ₃ of the first planetary carrier, the second planetary carrier, the third ring gear and the fourth ring gear is not 0, and the steering For the reverse direction, the first driving member and the second driving member control the ratio of the rotational speed N ₁ of the first sun gear to the rotational speed N ₂ of the third sun gear to be greater than P, and the steering is both forward, at this time The rotation speed _N6 of the output member is reversed. In order to avoid the situation that the rotation speed _N6 of the output member is reversed, the first planetary carrier, the second planetary carrier, and the second planetary carrier A one-way stopper is provided on the connecting body of the same rotation speed connecting the third ring gear and the fourth ring gear, and the one-way stopper restricts the first planetary carrier, the second planetary carrier, the third The rotation of the rotation speed _N3 of the ring gear and the fourth ring gear can only be forward, not reverse, so that the rotation of the rotation speed _N6 of the output member is always forward.

As a further description of the present invention, in the state D, the first driving member and the second driving member control the rotation speed _N1 of the first sun gear and the rotation speed _N2 of the third sun gear The ratio is 1, and the steering is positive, so that the rotational speed _N6 of the output member is equal to the rotational speed _N1 of the first sun gear and the rotational speed _N2 of the third sun gear, and the steering is positive , the transmission ratio at this time is 1.

As a further description of the present invention, in the state E, the first driving member and the second driving member control the rotation speed _N1 of the first sun gear and the rotation speed _N2 of the third sun gear If the ratio is less than 1, the steering is positive, and the rotation speed N ₆ of the output member is greater than the rotation speed N ₁ of the first sun gear and the rotation speed N ₂ of the third sun gear, and the rotation is positive.

As a further description of the present invention, when the first driving member fails, the second driving member drives the third sun gear at a speed of N ₂ , and the steering direction is positive, and the first planetary carrier, the The rotation speed _N3 of the second planet carrier, the third ring gear and the fourth ring gear has a tendency to reverse, and at this time, the one-way stopper restricts its reverse rotation, so that the first planet carrier, the second ring gear The rotation speed _N3 of the second planetary carrier, the third ring gear and the fourth ring gear is 0, the rotation speed _N6 of the output member is forward rotation, and the power of the second driving member passes through the third planetary row and The fourth planetary row decelerates and increases torque output.

As a further description of the present invention, when the second driving member fails, the first driving member drives the first sun gear at a speed of N ₁ , and the steering direction is positive, and the first planetary carrier, the The rotation speed _N3 of the second planet carrier, the third ring gear and the fourth ring gear tends to be reversed, and at this time, the one-way stopper restricts its reverse rotation, so that the first planet carrier, the The rotation speed N ₃ of the second planet carrier, the third ring gear and the fourth ring gear is 0, the rotation speed N ₆ of the output member is forward rotation, and the power of the first driving member passes through the first planetary row , The second planetary row and the fourth planetary row decelerate and increase the torque output.

The four-planet row continuously variable transmission mechanism and its speed change method provided by the present invention, through the adjustment of the rotational speed of the first driving member and the second driving member, and through the first planetary row, the second planetary row, the second planetary row The cooperation between the three planetary rows, the fourth planetary row and the one-way stopper changes the transmission ratio between the input end and the output end, and realizes the stepless speed change at the output end. The speed change mechanism has high transmission efficiency and large output torque. , no power interruption, simple and reliable structure, low manufacturing cost, easy maintenance and simple and convenient speed regulation. In addition, the four planetary row continuously variable transmission mechanism with unilateral staged transmission of the present invention is provided with a transmission stage between the second input shaft and the transmission shaft. The purpose of the size of the transmission ratio between the second driving member and the third sun gear, therefore, on the premise of achieving the same use effect, the transmission ratio provided by the transmission stage widens the power selection range of the second driving member.

Description of drawings

Fig. 1 is a schematic diagram of a four-planet row continuously variable transmission mechanism of a unilateral staged transmission provided by an embodiment of the present invention;

Fig. 2 is the rotational speed vector diagram of the first planetary row, the second planetary row, the third planetary row and the fourth planetary row provided by the embodiment of the present invention;

Fig. 3 is a rotational speed vector diagram combining the first planetary row, the second planetary row, the third planetary row and the fourth planetary row according to an embodiment of the present invention;

Fig. 4 is a rotational speed vector diagram when the ratio of the rotational speed _N1 of the first sun gear to the rotational speed _N2 of the third sun gear is less than P according to an embodiment of the present invention;

Fig. 5 is a rotational speed vector diagram when the ratio between the rotational speed _N1 of the first sun gear and the rotational speed _N2 of the third sun gear is greater than P according to an embodiment of the present invention;

Fig. 6 is a rotational speed vector diagram when the ratio of the rotational speed N ₁ of the first sun gear to the rotational speed N ₂ of the second sun gear is equal to 1 and the steering directions are both positive according to the embodiment of the present invention;

Fig. 7 is a rotational speed vector diagram when the ratio of the rotational speed N ₁ of the first sun gear to the rotational speed N ₂ of the second sun gear is less than 1 and the steering directions are both positive according to the embodiment of the present invention;

Fig. 8 is a rotational speed vector diagram when the rotational speed N ₁ of the first sun gear is constant and the rotational speed N ₂ of the third sun gear is adjusted according to the embodiment of the present invention;

Fig. 9 is a rotational speed vector diagram when the rotational speed N ₂ of the third sun gear is constant and the rotational speed N ₁ of the first sun gear is adjusted according to an embodiment of the present invention;

Fig. 10 is the rotational speed vector diagram when the steering of the third sun gear is positive when the first driving member fails according to the embodiment of the present invention;

Fig. 11 is a vector diagram of the rotational speed when the first driving member turns positive when the second driving member fails according to an embodiment of the present invention;

Fig. 12 is a rotational speed vector diagram when the ratio of the rotational speed N ₁ of the first sun gear to the rotational speed N ₂ of the third sun gear is equal to P and the steering is reversed according to the embodiment of the present invention.

Reference signs:

1-first planet row, 101-first sun gear, 102-first planet carrier, 103-first ring gear, 2-second planet row, 201-second sun gear, 202-second planet carrier, 203 -Second ring gear, 3-third planet row, 301-third sun gear, 302-third planet carrier, 303-third ring gear, 4-fourth planet row, 401-fourth sun gear, 402- The fourth planet carrier, 403-the fourth ring gear, 5-transmission stage, 501-transmission gear A, 502-transmission gear B, 6-first input shaft, 7-second input shaft, 8-first connecting shaft, 9-second connecting shaft, 10-output component, 11-one-way stopper, 12-transmission shaft.

Detailed ways

First of all, we will first explain the purpose of our declaration of the embodiment of the present invention. We are to solve the inherent problems of shifting frustration and power interruption in the AMT transmission; In order to expand the transmission ratio range, it is necessary to set a lot of gears, the shifting process is slow and the operation is complicated, which causes many drivers of large vehicles to be reluctant to step on the brakes; the shifting process of AMT transmission relies on complex control strategies, and it is difficult to grasp accurate There are problems such as high energy consumption and low efficiency when shifting gears; AMT transmissions have complex structures, high manufacturing costs, and difficult maintenance. Therefore, a four-planetary continuously variable transmission mechanism with unilateral staged transmission is proposed to solve the problem. Existing problems.

The embodiments of the present invention will be described in detail below in conjunction with the accompanying drawings. Let us first introduce the specific structures of the embodiments of the present invention.

Referring to Fig. 1, a four-planet row continuously variable transmission mechanism with unilateral staged transmission, including a first planetary row 1, a second planetary row 2, a third planetary row 3 and a fourth planetary row 4, on the third planetary row 3 The third sun gear 301 is connected to the transmission stage 5. The transmission stage 5 includes the transmission gear A501 and the transmission gear B502. The transmission gear A501 and the transmission gear B502 are meshed through external teeth, and the first ring gear 103 on the first planetary row 1 passes through the first The connecting shaft 8 is connected with the second sun gear 201 on the second planetary row 2, the second ring gear 203 on the second planetary row 2 is connected with the third planet carrier 302 on the third planetary row 3, and the third planetary row 3 The third planet carrier 302 on the top is connected to the fourth sun gear 401 on the fourth planetary row 4 through the second connecting shaft 9, and the fourth planetary carrier 402 on the fourth planetary row 4 is connected to the output member 10, and the first planetary The first planet carrier 102 on row 1, the second planet carrier 202 on the second planet row 2, the third ring gear 303 on the third planet row 3 and the fourth ring gear 403 on the fourth planet row 4 are all connected On the connecting body of the same speed, a one-way stopper 11 is arranged on the connecting body of the same speed, and the third sun gear 301 on the third planetary row 3 passes through the third planetary carrier 302 and the second connecting shaft through the transmission shaft 12 in turn. 9. The fourth sun gear 401, the fourth planet carrier 402 and the output member 10 are connected to the transmission gear A501, and the transmission gear B502 is connected to the second driving member through the second input shaft 7. The first sun gear on the first planetary row 1 101 passes through the first connecting shaft 8 , the second sun gear 201 , the third sun gear 301 , the transmission shaft 12 and the transmission gear A501 in turn through the first input shaft 6 and is connected to the first driving member.

Referring to Fig. 1, the first planetary row 1 includes a first sun gear 101, a first planetary carrier 102 and a first ring gear 103, and the second planetary row 2 includes a second sun gear 201, a second planetary carrier 202 and a second ring gear 203 , the third planetary row 3 includes the third sun gear 301 , the third planetary carrier 302 and the third ring gear 303 , and the fourth planetary row 4 includes the fourth sun gear 401 , the fourth planetary carrier 402 and the fourth ring gear 403 . In practical application, the first connecting shaft 8, the second sun gear 201, the third sun gear 301, the third planet carrier 302, the second connecting shaft 9, the fourth sun gear 401, the fourth planet carrier 402, the output member 10 , the transmission shaft 12 and the transmission gear A501 are all through hollow structures. The one-way stopper 11 is used to limit the rotation directions of the first planet carrier 102 , the second planet carrier 202 , the third ring gear 303 and the fourth ring gear 403 .

Next, we need to combine the specific structure of the embodiment of the present invention to illustrate the speed change method of the four-planet row continuously variable transmission mechanism based on the unilateral stepped transmission.

According to the basic principle of planetary gears, if the speed of any two of the three components of the sun gear, ring gear and planet carrier is determined, the speed of the other member is also determined, and their speed relationship is based on the number of teeth of the sun gear and the ring gear The number of teeth is in a corresponding proportional relationship.

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

Therefore, the rotational speed of the third sun gear 301 is N ₂ , the transmission ratio of the transmission stage 5 is i, the rotational speed of the second driving member is N ₂ ×i; the rotational speed of the first driving member is the same as the rotational speed of the first sun gear 101, set Set as N ₁ ; the rotational speeds of the first planet carrier 102, the second planet carrier 202, the third ring gear 303 and the fourth ring gear 403 are the same, set as N ₃ ; the first ring gear 103 and the second sun gear 201 The rotational speeds are the same, set as _N4 ; the rotational speeds of the second ring gear 203, the third planet carrier 302 and the fourth sun gear 401 are the same, set as _N5 ; the rotational speeds of the fourth planetary carrier 402 and the output member 10 are the same, set Set as N ₆ .

According to the speed vector calculation method of planetary gears, the speed vector diagrams of the first planetary row 1, the second planetary row 2, the third planetary row 3 and the fourth planetary row 4 are obtained, as shown in Fig. 2 . The length of the line segment in Figure 2 represents the size of the rotational speed, and the direction of the arrow represents the direction of the rotational speed. The upward direction of the arrow is defined as the forward steering, and the downward direction of the arrow is the reverse steering.

The rotational speed vector diagrams of the first planetary row 1, the second planetary row 2, the third planetary row 3 and the fourth planetary row 4 are combined to obtain the rotational speed vector diagram shown in FIG. 3 .

Referring to FIG. 3 , when any two values of N ₁ , N ₂ , N ₃ , N ₄ , N ₅ and N ₆ are determined, the other four values can be calculated from the proportional relationship of the line segments in the vector diagram. That is, the rotational speed N ₁ of the first driving member is determined, and the rotational speed N ₂ ×i of the second driving member is determined, so the rotational speed N ₆ of the output member 10 is also uniquely determined. By adjusting the rotational speed N ₁ of the first driving member and the rotational speed N ₂ of the second driving member ×i to control the rotational speed N ₁ of the first sun gear 101 and the rotational speed N ₂ of the third sun gear 301, the output member 10 can be controlled Continuous stepless change of the rotational speed N ₆ .

Next, the transmission principle of the four-planet row continuously variable transmission mechanism of the unilateral stepped transmission of the embodiment of the present invention will be described in conjunction with specific working conditions.

1. Starting conditions

Referring to Fig. 3, when starting, start to accelerate, the first drive member and the second drive member control the rotation speed N ₁ of the first sun gear 101 and the rotation speed N ₂ of the third sun gear 301 in terms of steering. On the one hand, control the ratio of the rotational speed N ₁ of the first sun gear 101 to the rotational speed N ₂ of the third sun gear 301 to be equal to P. The rotation speed _N6 of the output member 10 is gradually accelerated, and the steering is positive. Under this working condition, the power of the first driving part and the second driving part are coupled together, and the output is reduced by deceleration and increased torque, so that the vehicle accelerates to move forward.

2. Acceleration and deceleration conditions

Referring to Fig. 4, during acceleration and deceleration, the first driving member and the second driving member control the steering of the first sun gear 101 and the third sun gear 301 in the positive direction, and control the speed of the first sun gear 101 in terms of speed The ratio of _N1 to the rotational speed _N2 of the third sun gear 301 is smaller than P. The first driving member and the second driving member can realize the gradual increase of the rotating speed _N6 of the output member 10 by controlling the magnitude of the rotating speed _N1 of the first sun gear 101 and the rotating speed _N2 of the third sun gear 301 and the speed of increase and deceleration. Increase or decrease, the steering is forward, and the vehicle accelerates or decelerates to move forward.

In addition, as shown in Figure 8, the speed regulation method of acceleration and deceleration can also be to maintain the rotation speed _N1 of the first sun gear 101 through the first driving member, and to adjust the rotation speed N of the third sun gear 301 through the second driving member. ₂ to adjust the size of the rotational speed _N6 of the output member 10; as shown in Figure 9, it is also possible to maintain the rotational speed _N2 of the third sun gear 301 through the second driving member, and to adjust the first sun gear through the first driving member. The magnitude of the rotational speed _N1 of the wheel 101 is used to adjust the magnitude of the rotational speed _N6 of the output member 10 . Therefore, in the process of realizing the acceleration or deceleration of the rotation speed _N6 of the output member 10, the first drive member and the second drive member can be different according to their respective high-efficiency working areas, and the control system controls the first drive member and the second drive member according to the current working conditions Acceleration, deceleration and maintenance speed. In this way, both the first driving member and the second driving member can work in their respective high-efficiency working areas for a long time, thereby realizing the effect of energy saving.

3. Maximum speed condition

Referring to Fig. 6, the first driving member and the second driving member control the rotational speed N ₁ of the first sun gear 101 and the rotational speed N ₂ of the third sun gear 301 to be equal in magnitude, the steering direction is positive, and when both of them reach the highest rotational speed , the rotational speed _N6 of the output member 10 is also equal to the rotational speed _N1 of the first sun gear 101 and the rotational speed _N2 of the third sun gear 301, and it can be set that the vehicle reaches the maximum speed in this state.

Referring to Fig. 7, if the vehicle needs to reach a higher speed after reaching the above-mentioned maximum speed state, the rotational speed N ₁ of the first driving member can be reduced, and the rotational speed N ₁ of the first sun gear 101 will also be relatively reduced, and the second driving member maintains The rotation speed N ₂ of the third sun gear 301 remains unchanged at the highest rotation speed, so that the rotation speed N ₆ of the output member 10 continues to increase. The maximum vehicle speed is determined by _the rotational speed N ₆ of the output member 10 , which can be set by controlling the rotational speed N ₁ of the first driving member and the rotational speed N ₂ ×i of the second driving member. Therefore, as long as the second driving member with a lower rotating speed is selected, a very high output rotating speed can be achieved, which further reduces the power requirement for using the driving member.

Considering the above starting conditions and acceleration and deceleration conditions, there is a dangerous condition that needs to be considered how to avoid it.

Example: Referring to Fig. 5, when the rotational speed control of the first driving member and the second driving member is inaccurate or the control fails, the ratio of the rotational speed N ₁ of the first sun gear 101 to the rotational speed N ₂ of the third sun gear 301 is greater than P When the steering of the first sun gear 101 and the third sun gear 301 are both in the forward direction, the rotation speed _N6 of the output member 10 may turn in the reverse direction. At this time, the vehicle suddenly reverses, Severe accidents are extremely prone to occur. In order to prevent this from happening, a one-way stop is provided on the same-rotational connecting body connected together by the first planetary carrier 102, the second planetary carrier 202, the third ring gear 303 and the fourth ring gear 403. Actuator 11, to limit the rotation speed N ₃ of the first planetary carrier 102, the second planetary carrier 202, the third ring gear 303 and the fourth ring gear 403, the steering can only be forward, not reverse. This ensures that the rotation speed _N6 of the output member 10 is always positive. Therefore, when this dangerous working condition occurs, since the one-way stopper 11 restricts the rotation speed _N3 of the first planet carrier 102, the second planet carrier 202, the third ring gear 303 and the fourth ring gear 403, the steering can only be Forward, not reverse, at this time the first driving member and the second driving member will drag each other, the ratio of the rotational speed N ₁ of the first sun gear 101 to the rotational speed N ₂ of the third sun gear 301 is always equal to P, The rotation speed _N3 of the first planet carrier 102, the second planet carrier 202, the third ring gear 303 and the fourth ring gear 403 is equal to 0, so that the rotation speed _N6 of the output member 10 can only be positive, so the vehicle will not A sudden reverse driving situation occurred.

4. Reversing condition

Referring to Fig. 12, when reversing, start the first driving member and the second driving member to accelerate, and the first driving member and the second driving member control the first sun gear 101 and the third sun gear 301 in the direction of steering, both of which are reversed. In terms of speed, the ratio of the speed N ₁ of the first sun gear 101 to the speed N ₂ of the third sun gear 301 is controlled to be equal to P. The rotation speed _N6 of the output member 10 is gradually accelerated, and the steering is reversed. Under this working condition, the power of the first driving part and the second driving part are coupled together, and the output is reduced by deceleration and increased torque, so that the vehicle accelerates and runs backwards.

In addition to the above-mentioned normal working conditions and dangerous working conditions, there are also some emergency working conditions that need to be dealt with, which are taken into consideration and solved in the embodiments of the present invention.

Example: Referring to Fig. 10, when the first driving member fails, the second driving member drives the third sun gear 301 at a speed of N ₂ , and the steering direction is positive, the first planet carrier 102, the second planet carrier 202, and the third gear The rotation speed N ₃ of the ring 303 and the fourth ring gear 403 has a tendency to reverse, and at this time, the one-way stopper 11 restricts its reverse rotation, so that the first planet carrier 102, the second planet carrier 202, the third ring gear 303 and the second planet carrier The rotation speed _N3 of the four ring gear 403 is 0, the rotation speed _N6 of the output member 10 rotates in the forward direction, the power of the second driving member is output through the third planetary row 3 and the fourth planetary row 4 through deceleration and torque increase, so that the vehicle can continue to accelerate Or slow down and drive forward.

Referring to FIG. 11 , when the second driving member fails, the first driving member drives the first sun gear 101 at a speed of N ₁ , and the steering direction is positive. The first planet carrier 102 , the second planet carrier 202 , and the third ring gear 303 and the rotation speed N ₃ of the fourth ring gear 403 have a tendency to reverse, at this time the one-way stopper 11 restricts its reverse rotation, so that the first planet carrier 102, the second planet carrier 202, the third ring gear 303 and the fourth The rotation speed _N3 of the ring gear 403 is 0, the rotation speed _N6 of the output member 10 rotates in the forward direction, and the power of the first driving member is output through the first planetary row 1, the second planetary row 2 and the fourth planetary row 4 through deceleration and torque increase. Allows the vehicle to continue to accelerate or decelerate to move forward.

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

The four-planet row continuously variable transmission mechanism and its transmission method provided by the embodiment of the present invention have the following advantages:

1. The four-planet row continuously variable transmission mechanism with unilateral step-by-step transmission in the embodiment of the present invention has no power interruption during the speed regulation process, and runs quietly and stably. Users will have a better car experience when using the car. It can greatly meet the needs of customers in terms of sensory perception, and has laid a very good foundation for the promotion and use of this product.

2. The four-planet row continuously variable transmission mechanism of the unilateral staged transmission in the embodiment of the present invention can realize that the output end has a large torque from low speed to high speed, and realizes the ability of rapid acceleration and starting when the vehicle is driven by outputting a large torque. Moreover, the large torque can climb a larger slope when the vehicle is climbing, and the high torque can also meet the needs of more people, making this product more accessible.

3. The four-planet row stepless speed change mechanism of the unilateral staged transmission in the embodiment of the present invention can realize the stepless and continuous change of the output speed, and the driving part at the input end can work in the high-efficiency range for a long time, which improves the work efficiency and saves energy. In terms of use, more economical effects can be achieved, and more contributions can be made in terms of energy saving.

4. The four-planetary stepless speed change mechanism of the unilateral staged transmission in the embodiment of the present invention has simple and convenient speed regulation, and only needs to control the speed of the first driving part and the second driving part to realize the stepless continuous output speed Changes, thereby reducing the requirements of the vehicle on the control system, making the promotion and use of this product wider, and ensuring the promotion and popularity of this product to a certain extent.

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

6. Compared with the traditional driving method of a single driver, the product using the embodiment of the present invention can not only be driven by double drivers, but also can be matched with drivers with smaller volume and lower speed. The parts are more conducive to the layout design of the driving parts in the car body, which is more convenient for the beautiful design of the car body shape in the later stage, and the use of smaller driving parts can save costs.

7. The four-planet row continuously variable transmission mechanism with unilateral staged transmission in the embodiment of the present invention has a high-efficiency transmission rate. Under the same working conditions, a motor with lower power and lower speed can be selected as the driving member. Compared with large High-power batteries and low-power batteries can better prevent the occurrence of battery overheating, and the use safety of the battery is indirectly improved through the embodiments of the present invention.

8. The four-planet row continuously variable transmission mechanism of the unilateral staged transmission of the embodiment of the present invention adopts the four-planet row transmission, which increases the transmission ratio and further increases the torque, and can be applied to trucks with larger loads , muck trucks, passenger cars and other heavy-duty carts, further broadening the scope of application of the embodiments of the present invention.

9. In the four-planetary continuously variable transmission mechanism with unilateral staged transmission in the embodiment of the present invention, the connection ends of the first driving member, the second driving member and the output member are all set at one end of the continuously variable transmission mechanism, so that the power input Both the output and the output are at one end of the continuously variable transmission mechanism, and the first input shaft is connected to the first drive member through the second input shaft and the second drive member. This design can greatly improve the utilization of space, making The entire power equipment is more reasonable in arrangement and space utilization.

10. The four-planet row continuously variable transmission mechanism with unilateral step-by-step transmission in the embodiment of the present invention is provided with a transmission stage between the second input shaft and the transmission shaft. The transmission stage achieves The purpose of changing the transmission ratio between the second driving member and the third sun gear, therefore, on the premise of achieving the same use effect, the transmission ratio provided by the transmission stage broadens the power selection range of the second driving member.

The above-mentioned technical solutions only reflect the preferred technical solutions of the technical solutions of the present invention, and some changes that those skilled in the art may make to certain parts reflect the principles of the present invention and fall within the protection scope of the present invention.

Claims (12)

1. A single-side stepped transmission four-planet-row continuously variable transmission mechanism is characterized by comprising a first planet row (1), a second planet row (2), a third planet row (3) and a fourth planet row (4), wherein a third sun gear (301) on the third planet row (3) is connected with a transmission stage (5), the transmission stage (5) comprises a transmission gear A (501) and a transmission gear B (502), the transmission gear A (501) and the transmission gear B (502) are meshed through external teeth, a first ring gear (103) on the first planet row (1) is connected with a second sun gear (201) on the second planet row (2) through a first connecting shaft (8), a second ring gear (203) on the second planet row (2) is connected with a third planet carrier (302) on the third planet row (3), the third planet carrier (302) is connected with a fourth sun gear (401) on the fourth planet connecting shaft (4) through a second connecting shaft (9), a third planet carrier (403) on the third planet row (4) is connected with a third planet carrier (102), and a planet carrier (202) on the fourth planet row (3) is connected with a third planet carrier (102) output component (102) on the fourth planet row (3), and a third planet carrier (3) are connected with a third planet carrier (3) through a third planet carrier (3) and a third planet carrier (2) on the third planet carrier (3) and a third planet carrier (2) output ) All connect on the connector with the rotational speed, be provided with one-way stopper (11) on the connector with the rotational speed, third sun gear (301) pass through transmission shaft (12) in proper order third planet carrier (302), second connecting axle (9), fourth sun gear (401), fourth planet carrier (402) with output part (10) with drive gear A (501) are connected, drive gear B (502) are connected with the second driving piece through second input shaft (7), first sun gear (101) on first planet row (1) pass through first input shaft (6) in proper order first connecting axle (8), second sun gear (201) third sun gear (301) transmission shaft (12) with drive gear A (501) are connected with the first driving piece.

2. The single-side stepped transmission four-planetary-row continuously variable transmission mechanism according to claim 1, wherein the first connecting shaft (8), the second sun gear (201), the third sun gear (301), the third planet carrier (302), the second connecting shaft (9), the fourth sun gear (401), the fourth planet carrier (402), the output part (10), the transmission shaft (12) and the transmission gear A (501) are all of a through hollow structure.

3. The single-sided stage four-planetary-row continuously variable transmission according to claim 2, wherein the one-way stopper (11) is used to limit the rotation direction of the first carrier (102), the second carrier (202), the third ring gear (303), and the fourth ring gear (403).

4. A speed change method of a four-planet-row stepless speed change mechanism based on unilateral stepped transmission is characterized in that a first driving piece is connected with a first sun gear (101) through a first input shaft (6), so that the rotating speed of the first driving piece is the same as that of the first sun gear (101); the second driving piece is connected with the third sun gear (301) through a second input shaft (7), a transmission stage (5) and a transmission shaft (12), so that the rotating speed of the second driving piece and the rotating speed of the third sun gear (301) are in a proportional relation according to the transmission ratio of the transmission stage (5); a first planet carrier (102), a second planet carrier (202), a third gear ring (303) and a fourth gear ring (403) are all connected to a same-rotating-speed connecting body, so that the rotating speeds of the first planet carrier (102), the second planet carrier (202), the third gear ring (303) and the fourth gear ring (403) are the same; a first gear ring (103) and a second sun gear (201) are connected through a first connecting shaft (8), so that the rotating speed of the first gear ring (103) is the same as that of the second sun gear (201); the second ring gear (203) is connected with a third planet carrier (302), and the third planet carrier (302) is connected with a fourth sun gear (401) through a second connecting shaft (9), so that the rotating speeds of the second ring gear (203), the third planet carrier (302) and the fourth sun gear (401) are the same; the fourth planet carrier (402) is connected with the output component (10) so that the rotating speed of the fourth planet carrier (402) is the same as the rotating speed of the output component (10).

5. The speed change method of a four-planetary-row continuously variable transmission mechanism based on one-sided stepped transmission according to claim 4, characterized by setting: the rotating speed of the first driving part and the rotating speed of the first sun gear (101) are N ₁ (ii) a The rotating speed of the third sun gear (301) is N ₂ The transmission ratio of the transmission stage (5) is i, and the rotating speed of the second driving piece is N ₂ Xi, the rotational speeds of the first carrier (102), the second carrier (202), the third ring gear (303), and the fourth ring gear (403) are N ₃ The rotation speed of the first ring gear (103) and the rotation speed of the second sun gear (201) are N ₄ The second ring gear (203), the third planet carrier (302) and the fourth sun gear (401) have a rotational speed N ₅ The fourth planet carrier (402) and the output member (10) have a rotational speed N ₆ (ii) a When said N is ₁ 、N ₂ 、N ₃ 、N ₄ 、N ₅ 、N ₆ When any two values are determined, the other four values can be calculated through the proportional relation of line segments in the vector diagram; adjusting and controlling the rotational speed N of the first sun gear (101) by driving the first and second drive elements ₁ And the rotational speed N of the third sun gear (301) ₂ Realizing a rotational speed N of the output member (10) ₆ Wherein the first planet carrier (102), the second planet carrier (202), and the third planet carrier are continuously variable, whereinThe rotational speed N of the ring gear (303) and the fourth ring gear (403) ₃ When the rotational speed is 0, the rotational speed N of the first sun gear (101) is set ₁ And the rotational speed N of the third sun gear (301) ₂ The ratio of (A) to (B) is P; regulating the rotational speed N of the first sun gear (101) by driving the first drive element and the second drive element ₁ And the rotational speed N of the third sun gear (301) ₂ The output state of the output member (10) is made to include a state A, a state B, a state C, a state D and a state E.

6. The method for shifting a four-planetary-row continuously variable transmission mechanism based on one-sided step-gear according to claim 5, wherein in the state A, the rotation speeds N of the first carrier (102), the second carrier (202), the third ring gear (303) and the fourth ring gear (403) are N ₃ Is 0, the first driving part and the second driving part control the rotating speed N of the first sun gear (101) ₁ And the rotational speed N of the third sun gear (301) ₂ Is P, the rotation direction is positive, so that the rotation speed N of the output part (10) ₆ The steering of (1) is in the forward direction, and the transmission ratio is in the maximum state.

7. The method of claim 5, wherein in state B the speed N of the first planet carrier (102), the second planet carrier (202), the third ring gear (303) and the fourth ring gear (403) is ₃ The rotation direction is not 0, the rotation direction is the forward direction, and the first driving piece and the second driving piece control the rotation speed N of the first sun gear (101) ₁ And the rotational speed N of the third sun gear (301) ₂ Is less than P, the rotation directions are positive directions, so that the rotation speed N of the output part (10) ₆ The direction of rotation of (c) is the forward direction.

8. The method for shifting a four-planetary-row continuously variable transmission mechanism based on one-sided step transmission according to claim 5, wherein in the state C, the first planet carrier (102), the second planet carrier (202), the first planet carrierThe rotational speeds N of the three ring gears (303) and the fourth ring gear (403) ₃ The rotation direction is reverse instead of 0, and the first driving piece and the second driving piece control the rotation speed N of the first sun gear (101) ₁ And the rotational speed N of the third sun gear (301) ₂ Is greater than P, the direction of rotation is positive, the speed N of the output member (10) being at this time ₆ Is reversed in order to avoid a rotational speed N of the output member (10) ₆ Is arranged on the same rotational speed connecting body connected with the first planet carrier (102), the second planet carrier (202), the third ring gear (303) and the fourth ring gear (403), a one-way stopper (11) is arranged on the same rotational speed connecting body, the one-way stopper (11) limits the rotational speed N of the first planet carrier (102), the second planet carrier (202), the third ring gear (303) and the fourth ring gear (403) ₃ Can only be in a forward direction but not in a reverse direction, so that the rotational speed N of the output member (10) is set ₆ The steering of (c) is always positive.

9. The method of claim 5, wherein in state D the first and second drive controls the speed N of the first sun gear (101) ₁ And the rotational speed N of the third sun gear (301) ₂ Is 1, the rotation directions are positive directions, so that the rotating speed N of the output part (10) ₆ With the rotational speed N of the first sun gear (101) ₁ And the rotational speed N of the third sun gear (301) ₂ Is equal in size, the direction of rotation is positive, and the transmission ratio is 1.

10. The method of claim 5, wherein in state E the first and second drive controls the speed N of the first sun gear (101) ₁ And the rotational speed N of the third sun gear (301) ₂ Is less than 1, the rotation directions are positive directions, so that the rotation speed N of the output part (10) ₆ Greater than the rotational speed N of the first sun gear (101) ₁ And the third phaseRotational speed N of the sun gear (301) ₂ The direction of rotation is the forward direction.

11. The method for changing the speed of a four-planetary-row continuously variable transmission mechanism based on one-sided step transmission as claimed in claim 5, wherein when the first driving element fails, the second driving element drives the third sun gear (301) at a speed N ₂ The rotational speed N of the first carrier (102), the second carrier (202), the third ring gear (303), and the fourth ring gear (403) in the forward direction ₃ The reverse rotation tendency is generated when a one-way stopper (11) limits the reverse rotation, and the rotating speed N of the first planet carrier (102), the second planet carrier (202), the third ring gear (303) and the fourth ring gear (403) is enabled ₃ Is 0, the rotational speed N of the output member (10) ₆ The power of the second driving piece is output in a speed reducing and torque increasing mode through the third planetary row (3) and the fourth planetary row (4).

12. The method for changing the speed of a four-planetary-row continuously variable transmission mechanism based on one-sided step transmission as claimed in claim 5, wherein when the second driving element fails, the first driving element drives the first sun gear (101) at a speed N ₁ The rotational speed N of the first carrier (102), the second carrier (202), the third ring gear (303), and the fourth ring gear (403) in the forward direction ₃ The rotation of the planetary gear set tends to be reversed, and the one-way stopper (11) limits the reverse rotation of the planetary gear set so that the rotation speed N of the first planetary carrier (102), the second planetary carrier (202), the third ring gear (303) and the fourth ring gear (403) is equal to or higher than the rotation speed N of the planetary gear set ₃ Is 0, the rotational speed N of the output member (10) ₆ The power of the first driving piece is output in a speed reduction and torque increase mode through the first planet row (1), the second planet row (2) and the fourth planet row (4).

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