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

Abstract

The present invention discloses a hybrid three-planet gear continuously variable transmission mechanism and a speed change method thereof, belonging to the technical field of continuously variable transmission, comprising a first planetary gear, a second planetary gear and a third planetary gear, wherein the first ring gear on the first planetary gear is connected to the second planetary gear carrier on the second planetary gear, the second planetary gear carrier is connected to the third sun gear on the third planetary gear carrier through a connecting shaft, the first planetary gear carrier on the first planetary gear carrier is connected to the second ring gear on the second planetary gear carrier and the third ring gear on the third planetary gear carrier; a one-way clutch F is arranged between the connecting body and the housing of the first planetary gear carrier, the second ring gear and the third ring gear; a clutch is arranged between the first connecting shaft and the second connecting shaft. The engine and the second motor in the hybrid three-planet gear continuously variable transmission mechanism of the present invention input power in stages, ensuring that the power of the engine can always be maintained in its own high-efficiency working area, reducing energy consumption and emissions, increasing fuel economy, and thus improving the cruising range.

Description

Technical Field

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

[0002] With the promotion of new energy vehicles, my country has become the world's largest new energy vehicle market. Hybrid vehicles refer to vehicles that use traditional fuels and are equipped with electric motors or engines to improve low-speed power output and fuel consumption.

[0003] At present, most hybrid automatic transmission systems are driven by a single motor and an engine, which has disadvantages such as low overall efficiency, high energy consumption, and poor climbing, which restricts the application and promotion of new energy electric vehicles. In order to achieve a speed of 0-120 kilometers per hour, if the speed is changed by the motor speed regulation alone, the efficient working area only occupies a small part, and the energy consumption is very large when encountering complex road conditions. If the motor works for a long time with high torque, the life of the motor and other aspects will be affected. Therefore, it is very necessary to design a hybrid system automatic transmission device that makes the car have stronger power and high-speed cruising ability, and takes the power and economy of the whole vehicle to a higher level. Summary of the invention

[0004] The purpose of the present invention is to solve the above problems and to design a hybrid three-planetary gear continuously variable transmission mechanism and a transmission method thereof.

[0005] To achieve the above-mentioned purpose, the technical solution of the present invention is a hybrid three-planetary gear continuously variable transmission mechanism, including a first planetary gear, a second planetary gear and a third planetary gear, the first ring gear on the first planetary gear is connected to the second planetary gear on the second planetary gear, the second planetary gear is connected to the third sun gear on the third planetary gear through a connecting shaft, the first planetary gear on the first planetary gear is connected to the second ring gear on the second planetary gear and the third ring gear on the third planetary gear; a one-way clutch F is arranged between the connecting body of the first planetary gear, the second ring gear and the third ring gear and the housing; the third planetary gear on the third planetary gear is connected to an output component, the first sun gear on the first planetary gear is connected to the first motor through a first input shaft, the second input shaft connected to the second sun gear on the second planetary gear passes through the first sun gear, the first input shaft and the first motor to be connected to the second motor, the second motor is connected to the engine through the second connecting shaft and the first connecting shaft, and a clutch C is arranged between the first connecting shaft and the second connecting shaft.

[0006] As a further illustration of the present invention, the first sun gear is meshed with a first planetary gear on its outer teeth, the first planetary gear is mounted on the first planet carrier, and the first planetary gear is meshed with an inner ring gear of the first gear ring;

[0007] The second sun gear has outer teeth meshed with second planetary gears, the second planetary gears are mounted on the second planet carrier, and the second planetary gears are meshed with inner ring teeth of the second gear ring;

[0008] The third sun gear has outer teeth meshed with a third planetary gear, the third planetary gear is mounted on the third planet carrier, and the third planetary gear is meshed with inner ring teeth of the third gear ring;

[0009] The first sun gear, the first input shaft and the first motor are all hollow structures.

[0010] As a further explanation of the present invention, the one-way clutch F is used to limit the rotation direction of the first planetary carrier, the second ring gear and the third ring gear. The one-way clutch F makes the rotation direction of the first planetary carrier, the second ring gear and the third ring gear only consistent with the direction of rotation of the second motor or the engine.

[0011] The present invention also provides a speed change method based on a hybrid three-planet gear continuously variable transmission mechanism, wherein a first motor and a first sun gear are connected through a first input shaft, so that the rotation speed of the first motor is the same as the rotation speed of the first sun gear; a second motor and a second sun gear are connected through a second input shaft, so that the rotation speed of the second motor is the same as the rotation speed of the second sun gear; an engine and the second motor are connected through a first connecting shaft, a clutch C, and a second connecting shaft, and when the clutch C is in an engaged state, the rotation speeds of the engine, the second motor, and the second sun gear are the same; a first planet carrier, a second gear ring, and a third gear ring are connected, so that the rotation speeds of the first planet carrier, the second gear ring, and the third gear ring are the same; a first gear ring, a second planet carrier, and a third sun gear are connected, so that the rotation speeds of the first gear ring, the second planet carrier, and the third sun gear are the same; an output component is connected to a third planet carrier, so that the rotation speeds of the third planet carrier and the output component are the same; by adjusting and controlling the rotation speeds of the first motor, the second motor, and the engine, a stepless and continuous change of the rotation speed of the output component is achieved, and in this process, the speed ratio will also change accordingly.

[0012] As a further illustration of the present invention, it is set that: the speed of the first sun gear is N1, the speed of the second sun gear is N2, the speed of the first ring gear, the second planetary carrier and the third sun gear is N3, the speed of the first planetary carrier, the second ring gear and the third ring gear is N4, and the speed of the third planetary carrier and the output component is N5. 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; wherein, when the speed N4 of the first planetary carrier, the second ring gear and the third ring gear is 0, the ratio of the speed N1 of the first sun gear to the speed N2 of the second sun gear is set to P, and the speeds of the first motor, the second motor and the engine are adjusted and controlled so that the output state of the output component includes state A, state B, state C, state D and state E.

[0013] As a further illustration of the present invention, in the pure electric mode, the clutch C is disengaged, the first motor drives the first sun gear at a speed of N1; the second motor drives the second sun gear at a speed of N2; by controlling the magnitude, direction, and acceleration / deceleration speed of the first sun gear and the second sun gear N2, the speed N5 of the output component is continuously changed;

[0014] In the hybrid mode, the clutch C is engaged, the first motor drives the first sun gear at a speed of N1, the engine drives the second sun gear at a speed of N2, and the rotor of the second motor is driven by the engine to idle; the engine speed is maintained in the most efficient speed range, and the speed N5 of the output component is continuously changed by controlling the size, direction and acceleration / deceleration speed N1 of the first motor driving the first sun gear.

[0015] As a further explanation of the present invention, in state A, the rotational speed N4 of the first planetary carrier, the second ring gear and the third ring gear is 0, the rotational speed N1 of the first sun gear driven by the first motor is in the reverse direction, and the clutch C is controlled to be disengaged or engaged, the rotational speed N2 of the second sun gear driven by the second motor or the engine is in the forward direction, and at this time, the ratio of the rotational speed N1 of the first sun gear to the rotational speed N2 of the second sun gear is P, so that the rotational speed N5 of the output component is in the forward direction, and the transmission ratio in this state is the largest.

[0016] As a further explanation of the present invention, in the state B, the rotational speed N4 of the first planetary carrier, the second ring gear and the third ring gear is not 0, and the direction is forward. The rotational speed N4 of the first sun gear driven by the first motor is N1, and the direction is reverse. The clutch C is controlled to be disengaged or engaged. The rotational speed N2 of the second sun gear driven by the second motor or the engine is N2, and the direction is forward. At this time, the ratio of the rotational speed N1 of the first sun gear to the rotational speed N2 of the second sun gear is less than P, so that the rotational speed N5 of the output component is forward.

[0017] As a further explanation of the present invention, in the state C, the first motor drives the first sun gear to gradually reduce its speed N1 from reverse rotation to 0, controlling the clutch C to disengage or engage, and the second motor or the engine drives the second sun gear to a speed N2, turning to a positive direction, so that the speed N5 of the output component increases and turns to a positive direction.

[0018] As a further explanation of the present invention, in the state D, the first motor drives the first sun gear to gradually increase its speed N1 from 0 and turn to the positive direction, controlling the clutch C to disengage or engage, and the second motor or the engine drives the second sun gear to have a speed N2 and turn to the positive direction, so that the speed N5 of the output component increases and turns to the positive direction. If the speed N1 of the first sun gear is the same as the speed N2 of the second sun gear in this state, the transmission ratio at this time is 1.

[0019] As a further explanation of the present invention, in the state E, the first motor drives the first sun gear to have a rotation speed of N1 and a reverse direction, and the clutch C is controlled to be disengaged or engaged; the second motor or the engine drives the second sun gear to have a rotation speed of N2 and a forward direction; the ratio of the rotation speed N1 of the first sun gear to the rotation speed N2 of the second sun gear is greater than P; the rotation speed N4 of the first planetary carrier, the second ring gear and the third ring gear is reversed, so that the rotation speed N5 of the output component is reversed. In order to prevent this from happening, a one-way clutch F is provided on the connector of the first planetary carrier, the second ring gear and the third ring gear to limit the rotation speed N4 of the first planetary carrier, the second ring gear and the third ring gear to only be forward and not reverse, thereby ensuring that the rotation speed N5 of the output component is always forward.

[0020] As a further illustration of the present invention, when the second motor and the engine stop working, the first motor drives the first sun gear to rotate at a speed N1, the direction is reverse, the clutch C is in a disengaged state, at this time, the speed N4 of the first planetary carrier, the second gear ring and the third gear ring has a tendency to reverse, the one-way clutch F limits the reverse rotation of the first planetary carrier, the second gear ring and the third gear ring, so that the speed N4 of the first planetary carrier, the second gear ring and the third gear ring is 0, the direction of the speed N5 of the output component is always forward, and the power of the first motor is output through the first planetary gear row and the third planetary gear row to reduce speed and increase torque;

[0021] When the first motor and the engine stop working, the second motor drives the second sun gear to rotate at a speed of N2, and the rotation direction is forward, and the clutch C is in a disengaged state. At this time, the rotation speeds N4 of the first planetary carrier, the second gear ring and the third gear ring have a tendency to reverse, and the one-way clutch F limits the reverse rotation of the first planetary carrier, the second gear ring and the third gear ring, so that the rotation speeds N4 of the first planetary carrier, the second gear ring and the third gear ring are 0, and the rotation direction of the rotation speed N5 of the output component is always forward, and the power of the second motor is output through the second planetary gear set and the third planetary gear set to reduce speed and increase torque;

[0022] When the first motor and the second motor stop working, the engine drives the second sun gear at a speed of N2, and the direction is forward, and the clutch C is in an engaged state. At this time, the speeds N4 of the first planetary carrier, the second ring gear and the third ring gear have a tendency to reverse. The one-way clutch F limits the reversal of the first planetary carrier, the second ring gear and the third ring gear, so that the speeds N4 of the first planetary carrier, the second ring gear and the third ring gear are 0, and the direction of the speed N5 of the output component is always forward, and the power of the engine is output through the second planetary gear row and the third planetary gear row for deceleration and torque increase.

[0023] The hybrid three-planetary gear continuously variable transmission mechanism and the speed change method thereof provided by the present invention realize continuously variable speed change of the output end by adjusting the rotation speeds of the first motor and the second motor, or by adjusting the rotation speeds of the first motor and the engine, and by coordinating the first planetary gear, the second planetary gear, the third planetary gear and the one-way clutch, thereby changing the transmission ratio between the input end and the output end. The engine and the second motor of the mechanism input power in stages, ensuring that the power of the engine can always be maintained in its own high-efficiency working area, reducing energy consumption and emissions, increasing fuel economy, and thereby improving cruising range. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Figure 1It is a schematic diagram of a hybrid three-planetary gear continuously variable transmission mechanism provided by an embodiment of the present invention;

[0025] Figure 2 is a speed vector diagram of the first planetary gear, the second planetary gear and the third planetary gear provided by an embodiment of the present invention;

[0026] Figure 3 is a speed vector diagram when the ratio of the speed N1 of the first sun gear to the speed N2 of the second sun gear provided by the embodiment of the present invention is equal to P;

[0027] Figure 4 is a speed vector diagram when the ratio of the speed N1 of the first sun gear to the speed N2 of the second sun gear provided by the embodiment of the present invention is less than P;

[0028] Figure 5 is a speed vector diagram when the speed N1 of the first sun gear provided by an embodiment of the present invention is 0;

[0029] Figure 6 is a speed vector diagram when the speed N1 of the first sun gear and the speed N2 of the second sun gear provided by an embodiment of the present invention are the same;

[0030] Figure 7 is a speed vector diagram when the ratio of the speed N1 of the first sun gear to the speed N2 of the second sun gear provided by the embodiment of the present invention is greater than P;

[0031] Figure 8 is a speed vector diagram of the starting phase in pure electric mode provided by an embodiment of the present invention;

[0032] Fig. 9 is a speed vector diagram in a low-speed phase in a pure electric mode provided by an embodiment of the present invention;

[0033] Fig.10 is a speed vector diagram in the medium and high speed stage of the hybrid mode provided by an embodiment of the present invention;

[0034] Fig.11 is a speed vector diagram of the highest vehicle speed stage in the hybrid mode provided by an embodiment of the present invention;

[0035] Fig.12 is a speed vector diagram under a safety protection condition provided by an embodiment of the present invention;

[0036] Fig.13 is a speed vector diagram under a reversing condition provided by an embodiment of the present invention;

[0037] Fig.14 is a speed vector diagram under a single-drive working condition of the first motor provided by an embodiment of the present invention;

[0038] Fig.15is a speed vector diagram under a single-drive working condition of the second motor provided by an embodiment of the present invention;

[0039] Fig.16 It is a speed vector diagram of an engine under a single driving condition provided by an embodiment of the present invention.

[0040] Reference numerals:

[0041] 1-first planetary row, 101-first sun gear, 102-first planetary carrier, 103-first ring gear, 2-second planetary row, 201-second sun gear, 202-second planetary carrier, 203-second ring gear, 3-third planetary row, 301-third sun gear, 302-third planetary carrier, 303-third ring gear, 4-one-way clutch F, 5-first connecting shaft, 6-clutch C, 7-second connecting shaft, 8-first input shaft, 9-second input shaft, 10-third connecting shaft, 11-output component. DETAILED DESCRIPTION

[0042] The embodiment of the present invention is described in detail below with reference to the accompanying drawings. We first introduce the specific structure of the embodiment of the present invention.

[0043] See also Figure 1 A hybrid three-planet row continuously variable transmission mechanism comprises a first planet row 1, a second planet row 2 and a third planet row 3, wherein a first ring gear 103 on the first planet row 1 is connected to a second planet carrier 202 on the second planet row 2, the second planet carrier 202 is connected to a third sun gear 301 on the third planet row 3 via a connecting shaft, the first planet carrier 102 on the first planet row 1 is connected to the second ring gear 203 on the second planet row 2 and the third ring gear 303 on the third planet row 3; the first planet carrier 102, the second ring gear 203 and the third ring gear 303 A one-way clutch F4 is arranged between the connecting body and the housing; the output component 11 is connected to the third planetary carrier 302 on the third planetary row 3, the first sun gear 101 on the first planetary row 1 is connected to the first motor through the first input shaft 8, the second input shaft 9 connected to the second sun gear 201 on the second planetary row 2 passes through the first sun gear 101, the first input shaft 8 and the first motor to be connected to the second motor, the second motor is connected to the engine through the second connecting shaft 7 and the first connecting shaft 5, and a clutch C6 is arranged between the first connecting shaft 5 and the second connecting shaft 7.

[0044] See also Figure 1 , the first sun gear 101 is meshed with the outer teeth of the first planetary gear, 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 gear ring 103;

[0045] The second sun gear 201 is meshed with the outer teeth of the second planetary gear, the second planetary gear is mounted on the second planet carrier 202, and the second planetary gear is meshed with the inner ring teeth of the second gear ring 203;

[0046] The third sun gear 301 is meshed with the outer teeth of the 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 gear ring 303;

[0047] The first sun gear 101, the first input shaft 8 and the first motor are all hollow structures.

[0048] See also Figure 1 The one-way clutch F4 is used to limit the rotation direction of the first planetary carrier 102, the second ring gear 203 and the third ring gear 303. The one-way clutch F4 makes the rotation direction of the first planetary carrier 102, the second ring gear 203 and the third ring gear 303 only consistent with the direction of rotation of the second motor or the engine.

[0049] Next, we need to explain a speed changing method based on a hybrid three-planetary gear continuously variable transmission mechanism in combination with the specific structure of an embodiment of the present invention.

[0050] According to the basic principle of planetary gears, if the speeds of any two of the three components, namely the sun gear, the ring gear and the planet carrier, are determined, the speed of the other component is also determined, and the speed relationship between them 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. Setting: the speed of the first sun gear 101 is N1, the speed of the second sun gear 201 is N2, the speed of the first ring gear 103, the second planet carrier 202 and the third sun gear 301 is N3, the speed of the first planet carrier 102, the second ring gear 203 and the third ring gear 303 is N4, and the speed of the third planet carrier 302 and the output component 11 is N5.

[0051] In pure electric mode, the clutch C6 is disengaged, and the first motor drives the first sun gear 101 to a speed of N1; the second motor drives the second sun gear 201 to a speed of N2; by controlling the size, direction, and acceleration / deceleration speed of the speed N1 of the first sun gear 101 and the speed N2 of the second sun gear 201, the speed N5 of the output component 11 can be changed continuously and steplessly.

[0052] In hybrid mode, clutch C6 is engaged, the engine is working, the second motor is not working, the first motor drives the first sun gear 101 at a speed of N1, the engine drives the second sun gear 201 at a speed of N2, and the rotor of the second motor is driven by the engine to idle; the engine speed N2 is maintained in the most efficient speed range, and the speed N5 of the output component 11 is continuously changed by controlling the size, direction and acceleration / deceleration speed N1 of the first motor driving the first sun gear 101.

[0053] See also Figure 2 According to the speed vector calculation method of the planetary gear, the speed vector diagrams of the first planetary gear row 1, the second planetary gear row 2 and the third planetary gear row 3 are obtained, as shown in FIG. Figure 2 As shown, the first ring gear 103, the second planet carrier 202 and the third sun gear 301 are connected together and have the same speed N3; the first planet carrier 102, the second ring gear 203 and the third ring gear 303 are connected together and have the same speed N4. The length of the line segment in the figure represents the size of the speed, and the direction of the arrow represents the direction of the speed. It is defined that the upward arrow is the positive direction and the downward arrow is the reverse direction.

[0054] The speed vector diagrams of the first planetary gear 1, the second planetary gear 2 and the third planetary gear 3 are combined to obtain Figure 3 ,like Figure 3 As shown, 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; wherein, when the speed N4 of the first planetary carrier 102, the second gear ring 203 and the third gear ring 303 is 0, the ratio of the speed N1 of the first sun gear 101 to the speed N2 of the second sun gear 201 is set to P. By adjusting and controlling the speeds of the first motor, the second motor and the engine, the output state of the output component 11 includes state A, state B, state C, state D and state E.

[0055] See also Figure 3 In state A, the speed N4 of the first planetary carrier 102, the second ring gear 203 and the third ring gear 303 is 0, the speed N1 of the first sun gear 101 driven by the first motor is reverse, the clutch C6 is controlled to be disengaged or engaged, the speed N2 of the second sun gear 201 driven by the second motor or the engine is forward, at this time, the ratio of the speed N1 of the first sun gear 101 to the speed N2 of the second sun gear 201 is P, so that the speed N5 of the output component 11 is forward, the vehicle accelerates forward, and the transmission ratio in this state is the largest.

[0056] See also Figure 4 In state B, the speed N4 of the first planetary carrier 102, the second ring gear 203 and the third ring gear 303 is not 0, and the direction of rotation is forward. The speed of the first sun gear 101 driven by the first motor is N1, and the direction of rotation is reverse. The clutch C6 is controlled to be disengaged or engaged. The speed of the second sun gear 201 driven by the second motor or the engine is N2, and the direction of rotation is forward. At this time, the ratio of the speed N1 of the first sun gear 101 to the speed N2 of the second sun gear 201 is less than P, so that the speed N5 of the output component 11 is turned in the forward direction, and the vehicle accelerates forward.

[0057] See also Figure 5In state C, the first motor drives the speed N1 of the first sun gear 101 to gradually decrease from reverse rotation to 0, and the clutch C6 is controlled to be disengaged or engaged. The second motor or engine drives the second sun gear 201 to a speed N2, and the steering is forward, so that the speed N5 of the output component 11 increases, the steering is forward, and the vehicle accelerates forward.

[0058] See also Figure 6 In state D, the first motor drives the first sun gear 101 to gradually increase its speed N1 from 0 and turn to the forward direction, controlling the clutch C6 to be disengaged or engaged, and the second motor or engine drives the second sun gear 201 to have a speed N2 and turn to the forward direction, so that the speed N5 of the output component 11 increases and turns to the forward direction, and the vehicle accelerates forward. If the speed N1 of the first sun gear 101 and the speed N2 of the second sun gear 201 are the same in this state, the transmission ratio at this time is 1.

[0059] See also Figure 7 In state E, the first motor drives the first sun gear 101 at a speed of N1, and the direction is reverse, and the clutch C6 is controlled to be disengaged or engaged. The second motor or engine drives the second sun gear 201 at a speed of N2, and the direction is forward. The ratio of the speed N1 of the first sun gear 101 to the speed N2 of the second sun gear 201 is greater than P. The direction of the speed N4 of the first planetary carrier 102, the second ring gear 203 and the third ring gear 303 is reversed, so that the direction of the speed N5 of the output component 11 will be reversed. In order to prevent this from happening, a one-way clutch F4 is provided on the connector of the first planetary carrier 102, the second ring gear 203 and the third ring gear 303 to limit the direction of the speed N4 of the first planetary carrier 102, the second ring gear 203 and the third ring gear 303 to only be forward and not reverse. In this way, it is ensured that the direction of the speed N5 of the output component 11 is always forward, so that the vehicle always moves forward.

[0060] Next, an optimal power distribution scheme that can cope with all working conditions in an embodiment of the present invention is introduced.

[0061] 1. Starting conditions

[0062] See also Figure 8In the starting stage, the pure electric mode is adopted, the clutch C6 is controlled to be disengaged, the first motor and the second motor are started and accelerated at the same time, the first motor drives the first sun gear 101 to rotate in the reverse direction at the speed N1, and the second motor drives the second sun gear 201 to rotate in the forward direction at the speed N2, so that the ratio of the speed N1 of the first sun gear 101 to the speed N2 of the second sun gear 201 is equal to P, so that the speed N5 of the output component 11 gradually increases, turns to the forward direction, and the vehicle accelerates forward. Under this working condition, the power of the first motor and the second motor is coupled together, and the output is decelerated and torque is increased, and the engine does not participate in the work under this working condition, because the use of the engine in the low speed zone will have the disadvantages of low efficiency and high emissions, so this situation is avoided, and at the same time, the advantage of the motor with large torque at low speed is fully utilized.

[0063] 2. Low speed condition

[0064] See also Fig. 9 In the low-speed stage, the pure electric mode is adopted, the clutch C6 is controlled to be separated, the first motor and the second motor work simultaneously, the first motor drives the first sun gear 101 to rotate in the reverse direction at the speed N1, and the second motor drives the second sun gear 201 to rotate in the forward direction at the speed N2, so that the ratio of the speed N1 of the first sun gear 101 to the speed N2 of the second sun gear 201 is equal to or less than P, and the speed N5 of the output component 11 is accelerated or decelerated by adjusting the size and acceleration and deceleration speed of the first motor speed N1 and the second motor speed N2, and the rotation is forward. In this working condition, the power of the first motor and the second motor is coupled together, and the output is decelerated and torque is increased, and the engine does not participate in the work in this working condition, because the use of the engine in the low-speed zone will have the disadvantages of low efficiency and high emissions, so this situation is avoided, and at the same time, the advantage of the motor with large torque at low speed is fully utilized.

[0065] 3. Medium and high speed conditions

[0066] See also Fig.10, the hybrid mode is adopted in the medium and high speed stage, the clutch C6 is controlled to be engaged, the first motor and the engine are working, the engine drives the second sun gear 201 to turn to the forward direction, the engine speed is always maintained near the high-efficiency speed, and the direction is forward. The first motor drives the first sun gear 101 to turn from reverse to decelerate to 0, and then accelerate from the forward direction to the same as the speed N2 of the second sun gear 201, so that the speed N5 of the output component 11 is gradually accelerated and turned to the forward direction. Under this working condition, the speed of the engine is always maintained near the high-efficiency speed. By adjusting the size, direction and acceleration and deceleration speed of the speed N1 of the first sun gear 101 by the first motor, the speed N5 of the output component 11 can be accelerated or decelerated, and the direction is forward. Under this working condition, the power of the first motor and the engine is coupled together for output. Since the engine always works in the high-efficiency zone during acceleration and deceleration, energy consumption and emissions are reduced, fuel economy is increased, and thus the cruising range is improved.

[0067] Maximum speed condition

[0068] See also Fig.11 , the hybrid mode is adopted in the highest speed stage, the clutch C6 is engaged, the first motor and the engine are working, the engine drives the second sun gear 201 to rotate in the positive direction, the engine speed is always maintained near the high-efficiency speed, the rotation is in the positive direction, and the first motor continues to increase the speed N1 of the first sun gear 101 to achieve the continued increase of the speed N5 of the output component 11, thereby achieving a higher vehicle speed. Under this working condition, because the engine speed is always in the high-efficiency zone, it is only increased by the first motor, so the energy consumption and emissions are reduced, the fuel economy is increased, and the cruising range is improved.

[0069] 5. Safety protection working conditions

[0070] See also Fig.12 , the rotation speed N1 of the first sun gear 101 driven by the first motor is in the reverse direction, and the rotation speed N2 of the second sun gear 201 driven by the second motor or the engine is in the forward direction. If the rotation speed N1 of the first sun gear 101 and the rotation speed N2 of the second sun gear 201 are not accurately controlled or the control fails, then the ratio of the rotation speed N1 of the first sun gear 101 to the rotation speed N2 of the second sun gear 201 will be greater than P, and the rotation speed N5 of the output component 11 will turn in the reverse direction. At this time, the vehicle will suddenly reverse and a serious accident is very likely to occur. In order to prevent this from happening, a one-way clutch F4 is provided on the connector of the first planetary carrier 102, the second ring gear 203 and the third ring gear 303 to limit the rotation speed N4 of the first planetary carrier 102, the second ring gear 203 and the third ring gear 303 to only be in the forward direction, not in the reverse direction. In this way, it is ensured that the rotation speed N5 of the output component 11 is always in the forward direction, so that the vehicle can only drive forward.

[0071] 6. Reversing conditions

[0072] See also Fig.13 The reversing condition is similar to the starting condition stage. The pure electric mode is used for reversing. The clutch C6 is controlled to be disengaged. The first motor and the second motor are started and accelerated at the same time. The first motor drives the rotation speed N1 of the first sun gear 101 to turn in the positive direction. The second motor drives the rotation speed N2 of the second sun gear 201 to turn in the reverse direction. The ratio of the rotation speed N1 of the first sun gear 101 to the rotation speed N2 of the second sun gear 201 is equal to P, so that the rotation speed N5 of the output component 11 gradually increases and turns negative, and the vehicle accelerates to move backward. If the first motor and the second motor do not accurately control the speed N1 of the first sun gear 101 and the speed N2 of the second sun gear 201 or the control fails, the ratio of the speed N1 of the first sun gear 101 to the speed N2 of the second sun gear 201 will be greater than P, and the speed N5 of the output component 11 will turn to the forward direction. At this time, the vehicle will suddenly move forward, which is very likely to cause a serious accident. In order to prevent this from happening, a one-way clutch F4 is set on the connecting body of the first planetary carrier 102, the second ring gear 203 and the third ring gear 303 to limit the speed N4 of the first planetary carrier 102, the second ring gear 203 and the third ring gear 303 to only turn to the reverse direction, not the forward direction. In this way, it is ensured that the speed N5 of the output component 11 always turns to the reverse direction, so that the vehicle can only move backward.

[0073] 7. Emergency conditions

[0074] 1) See Fig.14 When the second motor and the engine stop working, the first motor drives the first sun gear 101 to rotate at a speed of N1, the direction of rotation is reverse, and the clutch C6 is in a disengaged state. At this time, the speed N4 of the first planetary carrier 102, the second ring gear 203 and the third ring gear 303 has a tendency to reverse. The one-way clutch F4 will limit the reverse rotation of the first planetary carrier 102, the second ring gear 203 and the third ring gear 303, 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 direction of rotation of the speed N5 of the output component 11 is always forward, and the vehicle can continue to move forward. The power of the first motor is output through the first planetary gear row 1 and the third planetary gear row 3 to reduce speed and increase torque;

[0075] 2) See Fig.15When the first motor and the engine stop working, the second motor drives the second sun gear 201 to rotate at a speed of N2, the direction of rotation is forward, and the clutch C6 is in a disengaged state. At this time, the speed N4 of the first planetary carrier 102, the second gear ring 203 and the third gear ring 303 has a tendency to reverse. The one-way clutch F4 will limit the reverse rotation of the first planetary carrier 102, the second gear ring 203 and the third gear ring 303, so that the speed N4 of the first planetary carrier 102, the second gear ring 203 and the third gear ring 303 is 0, and the direction of rotation of the speed N5 of the output component 11 is always forward, and the vehicle can continue to move forward. The power of the second motor is output through the second planetary gear 2 and the third planetary gear 3 to reduce speed and increase torque;

[0076] 3) See Fig.16 When the first motor and the second motor stop working, the engine drives the second sun gear 201 at a speed of N2, the direction of rotation is forward, and the clutch C6 is engaged. At this time, the speed N4 of the first planetary carrier 102, the second ring gear 203 and the third ring gear 303 has a tendency to reverse. The one-way clutch F4 will limit the reverse rotation of the first planetary carrier 102, the second ring gear 203 and the third ring gear 303, 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 direction of rotation of the speed N5 of the output component 11 is always forward, the vehicle can continue to move forward, and the power of the engine is output through the second planetary gear 2 and the third planetary gear 3 to reduce speed and increase torque.

[0077] 8. Energy recovery conditions

[0078] When the vehicle is driving and braking, the first motor drags at the vehicle inertia speed. At this time, the first motor is used as a generator to convert the recovered energy into electrical energy and store it in the battery.

[0079] The hybrid three-planetary gear continuously variable transmission mechanism and the speed change method thereof provided by the embodiment of the present invention have the following advantages:

[0080] 1. The hybrid three-planetary gearbox continuously variable transmission mechanism of the embodiment of the present invention has no power interruption during the speed regulation process and runs quietly and smoothly. Users will have a better car experience when using the car, which can greatly meet customer needs in terms of sensory perception and lay a very good foundation for the promotion and use of this product.

[0081] 2. The hybrid three-planetary gearbox continuously variable transmission mechanism of the embodiment of the present invention can achieve large torque at the output end from low speed to high speed. By outputting large torque, the vehicle can have the ability to quickly accelerate and start when driving, and the large torque can climb a larger slope when the vehicle climbs. The large torque can also meet the car use needs of more people, making this product more popular.

[0082] 3. The hybrid three-planetary gear continuously variable transmission mechanism of the embodiment of the present invention can realize stepless and continuous change of the output speed, and the input end drive element can work in the high-efficiency range for a long time, thereby improving the working efficiency, achieving more economical effect in the use of energy, and making more contributions to energy saving.

[0083] 4. In the embodiment of the present invention, the power of the first motor and the second motor are coupled together to drive the vehicle, or the power of the first motor and the engine are coupled together to drive the vehicle. When any one or two of the first motor, the second motor and the engine fail, the other one or two can still drive the vehicle, which greatly increases the reliability of vehicle use and ensures that when the owner uses the car, even if one or two driving components fail, the owner can still rely on the remaining one or two driving components to drive the vehicle and drive the vehicle to the maintenance site in time, avoiding the occurrence of towing incidents and better taking care of the owner's car experience.

[0084] 5. The hybrid three-planetary gear continuously variable transmission mechanism of the embodiment of the present invention has a high efficiency transmission rate. Under the same working conditions, a motor with lower power and lower speed can be selected as a driving part. Compared with a high-power battery, a low-power battery can better prevent the occurrence of battery overheating. The embodiment of the present invention indirectly improves the safety of battery use.

[0085] 6. The hybrid three-planetary gear continuously variable transmission mechanism of the embodiment of the present invention adopts a three-planetary gear transmission, which increases the transmission ratio and further increases the torque. It can be used in heavy vehicles such as trucks, muck trucks, and buses with larger loads, further broadening the scope of application of the embodiment of the present invention.

[0086] 7. When the vehicle reaches medium or high speed conditions, the hybrid three-planetary gearbox continuously variable transmission mechanism of the embodiment of the present invention takes over the transmission of power from the second motor, ensuring that the power of the engine can always be maintained in its high-efficiency operating area, reducing energy consumption and emissions, increasing fuel economy, and thus improving cruising range.

[0087] 8. In the hybrid three-planetary gear continuously variable transmission mechanism of the embodiment of the present invention, when the vehicle is driving and braking, the first motor drags at the vehicle inertia speed. At this time, the first motor is used as a generator to convert the recovered energy into electrical energy and store it in the battery, thereby improving the energy utilization rate.

[0088] The above technical solutions only reflect the preferred technical solutions of the technical solutions of the present invention. Some changes that may be made to certain parts thereof by technicians in this technical field all reflect the principles of the present invention and fall within the protection scope of the present invention.

Claims

1. A hybrid three-planet gear continuously variable transmission mechanism, characterized in that: The invention comprises a first planetary gear (1), a second planetary gear (2) and a third planetary gear (3), wherein the first ring gear (103) on the first planetary gear (1) is connected to the second planetary gear carrier (202) on the second planetary gear (2), the second planetary gear carrier (202) is connected to the third sun gear (301) on the third planetary gear (3) via a connecting shaft, the first planetary gear carrier (102) on the first planetary gear (1) is connected to the second ring gear (203) on the second planetary gear (2) and the third ring gear (303) on the third planetary gear (3); a connecting body of the first planetary gear carrier (102), the second ring gear (203) and the third ring gear (303) A one-way clutch F (4) is arranged between the first planetary gear (3) and the housing; an output component (11) is connected to the third planetary carrier (302) on the third planetary gear (3); the first sun gear (101) on the first planetary gear (1) is connected to the first motor via a first input shaft (8); the second input shaft (9) connected to the second sun gear (201) on the second planetary gear (2) passes through the first sun gear (101), the first input shaft (8) and the first motor to be connected to the second motor; the second motor is connected to the engine via a second connecting shaft (7) and the first connecting shaft (5); a clutch C (6) is arranged between the first connecting shaft (5) and the second connecting shaft (7); The first sun gear (101) is meshed with a first planetary gear on its outer teeth, the first planetary gear is mounted on the first planet carrier (102), and the first planetary gear is meshed with an inner ring gear of the first ring gear (103); The second sun gear (201) is meshed with a second planetary gear on its outer teeth, the second planetary gear is mounted on the second planet carrier (202), and the second planetary gear is meshed with an inner ring gear of the second ring gear (203); The third sun gear (301) is meshed with a third planetary gear on its outer teeth, the third planetary gear is mounted on the third planet carrier (302), and the third planetary gear is meshed with the inner ring teeth of the third gear ring (303); The first sun gear (101), the first input shaft (8) and the first motor are all hollow structures; The one-way clutch F (4) is used to limit the rotation direction of the first planetary carrier (102), the second ring gear (203) and the third ring gear (303). The one-way clutch F (4) makes the rotation direction of the first planetary carrier (102), the second ring gear (203) and the third ring gear (303) only consistent with the rotation direction of the second motor or the engine.

2. A speed changing method based on the hybrid three-planet gear continuously variable transmission mechanism according to claim 1, characterized in that: The first motor and the first sun gear (101) are connected via a first input shaft (8), so that the rotation speed of the first motor is the same as the rotation speed of the first sun gear (101); the second motor and the second sun gear (201) are connected via a second input shaft (9), so that the rotation speed of the second motor is the same as the rotation speed of the second sun gear (201); the engine and the second motor are connected via a first connecting shaft (5), a clutch C (6) and a second connecting shaft (7), and when the clutch C (6) is in an engaged state, the rotation speeds of the engine, the second motor and the second sun gear (201) are the same; the first planetary carrier (102), the second ring gear (203) and the third ring gear (303) are connected, The first planetary carrier (102), the second ring gear (203) and the third ring gear (303) have the same rotational speed; the first ring gear (103), the second planetary carrier (202) and the third sun gear (301) are connected so that the first ring gear (103), the second planetary carrier (202) and the third sun gear (301) have the same rotational speed; the output component (11) is connected to the third planetary carrier (302) so that the third planetary carrier (302) and the output component (11) have the same rotational speed; and the rotational speed of the output component (11) is continuously changed by adjusting and controlling the rotational speeds of the first motor, the second motor and the engine, and in this process, the speed ratio will also change accordingly.

3. The speed changing method of the hybrid three-planet gear continuously variable transmission mechanism according to claim 2, characterized in that: Assume that: the speed of the first sun gear (101) is N1, the speed of the second sun gear (201) is N2, the speed of the first ring gear (103), the second planet carrier (202) and the third sun gear (301) is N3, the speed of the first planet carrier (102), the second ring gear (203) and the third ring gear (303) is N4, the speed of the third planet carrier (302) and the output component (11) is N5, when any two values ​​of N1, N2, N3, N4 and N5 are determined When the rotation speed N4 of the first planetary carrier (102), the second gear ring (203) and the third gear ring (303) is 0, the ratio of the rotation speed N1 of the first sun gear (101) to the rotation speed N2 of the second sun gear (201) is set to P, and the output state of the output component (11) includes state A, state B, state C, state D and state E by adjusting and controlling the rotation speeds of the first motor, the second motor and the engine.

4. The speed changing method of the hybrid three-planet gear continuously variable transmission mechanism according to claim 3, characterized in that: In pure electric mode, the clutch C (6) is disengaged, and the first motor drives the first sun gear (101) at a speed of N1; The second motor drives the second sun gear (201) to have a rotation speed N2; by controlling the magnitude, direction, and acceleration / deceleration speed N1 of the first sun gear (101) and the rotation speed N2 of the second sun gear (201), the rotation speed N5 of the output component (11) is continuously changed in a stepless manner; In the hybrid mode, the clutch C (6) is engaged, the first motor drives the first sun gear (101) at a speed of N1, the engine drives the second sun gear (201) at a speed of N2, and the rotor of the second motor is driven by the engine to idle; the engine speed is maintained in the most efficient speed range, and the speed N5 of the output component (11) is continuously changed by controlling the size, direction and acceleration / deceleration speed of the speed N1 driven by the first motor to drive the first sun gear (101).

5. The speed changing method of the hybrid three-planet gear continuously variable transmission mechanism according to claim 4, characterized in that: In the state A, 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 N1 of the first sun gear (101) driven by the first motor is reverse, the clutch C (6) is controlled to be disengaged or engaged, the rotation speed N2 of the second sun gear (201) driven by the second motor or the engine is forward, at which time the ratio of the rotation speed N1 of the first sun gear (101) to the rotation speed N2 of the second sun gear (201) is P, so that the rotation speed N5 of the output component (11) is forward, and the transmission ratio in this state is the largest.

6. The speed changing method of the hybrid three-planet gear continuously variable transmission mechanism according to claim 4, characterized in that: In the state B, the rotation speed N4 of the first planetary carrier (102), the second ring gear (203) and the third ring gear (303) is not 0, and the direction of rotation is forward. The rotation speed N1 of the first sun gear (101) driven by the first motor is reverse, and the clutch C (6) is controlled to be disengaged or engaged. The rotation speed N2 of the second sun gear (201) driven by the second motor or the engine is forward. At this time, the ratio of the rotation speed N1 of the first sun gear (101) to the rotation speed N2 of the second sun gear (201) is less than P, so that the rotation speed N5 of the output component (11) is forward.

7. The speed changing method of the hybrid three-planet gear continuously variable transmission mechanism according to claim 4, characterized in that: In the state C, the first motor drives the first sun gear (101) to gradually reduce its speed N1 from reverse rotation to 0, controlling the clutch C (6) to be disengaged or engaged, and the second motor or the engine drives the second sun gear (201) to a speed N2, which is turned in a positive direction, so that the speed N5 of the output component (11) increases and turns in a positive direction.

8. The speed changing method of the hybrid three-planet gear continuously variable transmission mechanism according to claim 4, characterized in that: In the state D, the first motor drives the first sun gear (101) to gradually increase its rotation speed N1 from 0 and turn to the positive direction, controlling the clutch C (6) to be disengaged or engaged, and the second motor or the engine drives the second sun gear (201) to have a rotation speed N2 and turn to the positive direction, so that the rotation speed N5 of the output component (11) increases and turns to the positive direction. If the rotation speed N1 of the first sun gear (101) and the rotation speed N2 of the second sun gear (201) are the same in this state, the transmission ratio at this time is 1.

9. The speed changing method of the hybrid three-planet gear continuously variable transmission mechanism according to claim 4, characterized in that: In the state E, the first motor drives the first sun gear (101) at a speed of N1, the direction of rotation is reverse, and the clutch C (6) is controlled to be disengaged or engaged; the second motor or the engine drives the second sun gear (201) at a speed of N2, the direction of rotation is forward, the ratio of the speed N1 of the first sun gear (101) to the speed N2 of the second sun gear (201) is greater than P, and the speeds N of the first planetary carrier (102), the second gear ring (203) and the third gear ring (303) are greater than P. 4 is in the reverse direction, causing the rotation speed N5 of the output component (11) to be in the reverse direction. In order to prevent this from happening, a one-way clutch F (4) is provided on the connecting body of the first planetary carrier (102), the second ring gear (203) and the third ring gear (303), so as to limit the rotation speed N4 of the first planetary carrier (102), the second ring gear (203) and the third ring gear (303) to be in the forward direction only and not in the reverse direction, thereby ensuring that the rotation speed N5 of the output component (11) is always in the forward direction.

10. The speed changing method of the hybrid three-planet gear continuously variable transmission mechanism according to claim 9, characterized in that: When the second motor and the engine stop working, the first motor drives the first sun gear (101) to rotate at a speed N1, and the direction of rotation is reverse, and the clutch C (6) is in a disengaged state. At this time, the rotation speed N4 of the first planetary carrier (102), the second gear ring (203) and the third gear ring (303) has a tendency to reverse, and the one-way clutch F (4) limits the reverse rotation of the first planetary carrier (102), the second gear ring (203) and the third gear ring (303), so that the rotation speed N4 of the first planetary carrier (102), the second gear ring (203) and the third gear ring (303) is 0, and the direction of rotation of the rotation speed N5 of the output component (11) is always forward, and the power of the first motor is output through the first planetary gear (1) and the third planetary gear (3) to reduce speed and increase torque; When the first motor and the engine stop working, the second motor drives the second sun gear (201) to rotate at a speed of N2, with the rotation direction being positive, and the clutch C (6) is in a disengaged state. At this time, the rotation speed N4 of the first planetary carrier (102), the second gear ring (203) and the third gear ring (303) has a tendency to reverse, and the one-way clutch F (4) limits the reverse rotation of the first planetary carrier (102), the second gear ring (203) and the third gear ring (303), so that the rotation speed N4 of the first planetary carrier (102), the second gear ring (203) and the third gear ring (303) is 0, and the rotation direction of the rotation speed N5 of the output component (11) is always positive, and the power of the second motor is output through the second planetary gear set (2) and the third planetary gear set (3) to reduce speed and increase torque; When the first motor and the second motor stop working, the engine drives the second sun gear (201) to rotate at a speed N2, with the rotation direction being positive, and the clutch C (6) is in an engaged state. At this time, the rotation speed N4 of the first planetary carrier (102), the second ring gear (203) and the third ring gear (303) has a tendency to reverse. The one-way clutch F (4) limits the reverse rotation of the first planetary carrier (102), the second ring gear (203) and the third ring gear (303), so that the rotation speed N4 of the first planetary carrier (102), the second ring gear (203) and the third ring gear (303) is 0, and the rotation direction of the rotation speed N5 of the output component (11) is always positive, and the power of the engine is output through the second planetary gear (2) and the third planetary gear (3) to reduce speed and increase torque.

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