WO2023159533A1 - Mechanical and electrical continuously variable speed composite transmission system and control method thereof - Google Patents

Abstract

Disclosed in the present invention are a mechanical and electrical continuously variable speed composite transmission system and a control method thereof. The system comprises an input shaft assembly, a mechanical transmission assembly, an electric transmission assembly and an output shaft assembly. Switching among a single-flow transmission mode, a composite transmission mode and an energy recovery mode is achieved by means of combinational switching between a clutch and a brake, the single-flow transmission mode comprising an EVT transmission mode and a mechanical transmission mode, and the composite transmission mode being an EVT-mechanical composite transmission mode. Beneficial effects: the present invention may adapt to different working conditions, increase the engine power utilization rate, improve fuel economy, effectively reduce shift jerks, and enlarge a speed ratio adjustment range; in the aspect of power adjustment, the electric transmission assembly can effectively supplement driving force by means of an energy storage device, and an EVT can also recover energy generated during braking; and the present invention effectively widens a speed regulation range, and thus may satisfy the requirements for linear and nonlinear stepless speed regulation in a large range.

Description

A compound transmission system with mechanical and electrical stepless speed change and its control method technical field

The invention relates to a transmission system and a control method thereof, in particular to a mechanical-electrical stepless-variable composite transmission system and a control method thereof, which belong to the technical field of variable-speed transmission devices.

Background technique

Automobile transmission is the core component of automobile transmission system and one of the important evaluation indicators of vehicle performance. During the running of the car, the car transmission changes the transmission ratio between the engine and the driving wheels, so that the engine always works at its best power performance state, adapting to different forms of starting, accelerating, driving and overcoming various road obstacles. Different requirements for driving wheel traction and vehicle speed under different conditions.

When the oil of the hydraulic mechanism in the traditional machine-hydraulic continuously variable transmission is mixed into the air, it is easy to cause vibration and noise, which affects the working performance of the system, and the oil of the hydraulic mechanism is easily polluted. When the oil is polluted, it will affect the system. work reliability.

Electric continuously variable transmission (EVT) is an advanced technology developed in recent years. It provides vehicles with continuously variable speed, making the driving more stable and comfortable. When the electric continuously variable transmission and the internal combustion engine are effectively controlled and coordinated, the fuel efficiency of the vehicle can be greatly improved. In terms of power adjustment, EVT can effectively supplement the driving force through the accumulator without changing the power requirements of the internal combustion engine, so as to keep the working state of the internal combustion engine from being affected by road conditions and improve the efficiency of the vehicle. However, when the EVT is directly connected to the output shaft, it will encounter the problem of EVT overheating at higher speeds, so the single EVT transmission mode cannot meet the transmission needs of multiple working conditions.

Contents of the invention

Purpose of the invention: Aiming at the deficiencies in the prior art, the present invention provides a compound transmission system of mechanical and electrical stepless transmission and its control method. The present invention realizes EVT transmission, mechanical transmission, Mechanical-EVT compound transmission and switching of multiple modes of energy recovery; it can adapt to different working conditions, improve engine power utilization and improve fuel economy.

Technical solution: a compound transmission system with mechanical and electrical stepless speed change,

including an input shaft assembly including an input shaft, a first clutch _C1 and an input gear pair;

A mechanical transmission assembly, the mechanical transmission assembly includes a mechanical transmission shaft, a front planetary row assembly, a rear planetary row assembly, a fifth clutch C ₅ , a first brake B ₁ and a second brake B ₂ , the front planetary row assembly includes a front Sun gear, front planetary carrier, front ring gear, described rear planetary row assembly comprises rear sun gear, rear planetary carrier and rear ring gear; Described mechanical transmission shaft is connected with input shaft through first clutch _C1 , and described mechanical transmission Shafts are respectively fixedly connected to the front ring gear and the rear sun gear, the front planet carrier is connected to the rear planet carrier, the front sun gear is connected to the mechanical transmission shaft through the fifth clutch _C5 , and the first brake _B1 can be locked For the front sun gear, the second brake _B2 can simultaneously lock the front planetary carrier and the rear planetary carrier;

An electric transmission assembly, the electric transmission assembly includes an electric input shaft, an inner rotor, an outer rotor, a stator, a power supply, an electric output shaft, a second clutch C ₂ and a third clutch C ₃ ; the input gear pair passes through the second clutch C _2. Connected to the electric input shaft, the electric input shaft is connected to the inner rotor, the electric output shaft is connected to the outer rotor, the power supply supplies power to the stator to generate a magnetic field, and the magnetic field generated by the stator controls the transmission speed of the inner rotor relative to the outer rotor Ratio, to realize the adjustment of the transmission speed ratio of the electric input shaft relative to the electric output shaft;

An output shaft assembly, the output shaft assembly includes an output shaft, an output sun gear, an output planet carrier, an output ring gear, an output gear pair and a fourth clutch _C4 ; the output sun gear is connected with the rear ring gear, and the output gear The ring is connected to the third clutch _C3 through the output gear pair, the output planet carrier is connected to the output shaft, and the output sun gear is connected to the output shaft through the fourth clutch _C4 .

The present invention realizes the switching of multiple modes of EVT transmission, mechanical transmission, mechanical-EVT compound transmission and energy recovery by switching the clutch assembly and the brake assembly; it can adapt to different working conditions, improve engine power utilization, and improve fuel economy; effectively The impact of shifting is greatly reduced, and the range of speed ratio adjustment is increased; in terms of power adjustment, the electric transmission component can effectively supplement the driving force through the energy storage, and the EVT can also recover the energy during braking and send it back to the energy storage. Middle: The power-split mechanical-EVT compound transmission system of the present invention has a mechanical-EVT parallel transmission mode, which effectively broadens the speed regulation range and can meet the requirements of large-scale linear and nonlinear stepless speed regulation.

Preferably, in order to realize the recovery of braking energy while supplementing the driving power, the electric transmission assembly includes a slip ring, the slip ring is connected to the inner rotor, the inner rotor converts mechanical energy into electrical energy, and the generated electrical energy passes through the slip ring delivered to the power supply.

A control method for a mechanically and electrically continuously variable compound transmission system, which realizes switching between a single-flow transmission mode, a compound transmission mode and an energy recovery mode through combined switching between a clutch and a brake; the single-flow transmission mode includes EVT transmission mode and mechanical transmission mode; the compound transmission mode is EVT and mechanical compound transmission mode.

The engagement elements of each transmission mode are shown in Table 1. details as follows:

Table 1 Mode switching element engagement state

Note: ▲ means the actuator is in the engaged state, △ means the actuator is in the disengaged state.

Preferably, the control method of the EVT transmission mode is as follows:

The second clutch C ₂ , the third clutch C ₃ and the fourth clutch C ₄ are engaged, while the first clutch C ₁ , the fifth clutch C ₅ , the first brake B ₁ and the second brake B ₂ are disengaged; the power passes through the input shaft Input gear pair, second clutch C ₂ , electric input shaft, inner rotor, outer rotor, electric output shaft, third clutch C ₃ , output gear pair, output ring gear, output planet carrier to output shaft output.

Preferably, the mechanical transmission mode includes mechanical transmission 1st gear, mechanical transmission 2nd gear and mechanical transmission 3rd gear, and the specific control method is as follows:

Mechanical transmission 1st gear (M1): the first clutch C ₁ , the fourth clutch C ₄ and the first brake B ₁ are engaged, while the second clutch C ₂ , the third clutch C ₃ , the fifth clutch C ₅ and the second brake B ₂ Separation; the power is from the input shaft to the mechanical transmission shaft through the first clutch _C1 , and the power is divided by the mechanical transmission shaft. One route is from the front ring gear, the front planetary carrier to the rear planetary carrier, and the other route is from the rear sun gear to the rear planetary carrier. The two-way power is merged in the rear planetary carrier, and then output from the rear ring gear, the fourth clutch _C4 to the output shaft;

Mechanical transmission 2nd gear (M2): the first clutch C ₁ , the fourth clutch C ₄ and the fifth clutch C ₅ are engaged, while the second clutch C ₂ , the third clutch C ₃ , the first brake B ₁ and the second brake B ₂ Separation; the power is sent from the input shaft to the mechanical transmission shaft through the first clutch _C1 , and the power is divided by the mechanical transmission shaft. The first route is from the fifth clutch _C5 and the front sun gear to the front planetary carrier, and the second route is from the front ring gear to the front Planetary carrier, the power of the first and second channels is combined to the rear planetary carrier, the third route is from the rear sun gear to the rear planetary carrier, the power is combined in the rear planetary carrier, and then from the rear ring gear, the fourth clutch C ₄ to the output shaft output;

Mechanical transmission 3rd gear (M3): the first clutch C ₁ , the fourth clutch C ₄ and the second brake B ₂ are engaged, while the second clutch C ₂ , the third clutch C ₃ , the fifth clutch C ₅ and the first brake B ₁ Separation; the power is output from the input shaft through the first clutch C ₁ , the mechanical transmission shaft, the rear sun gear, the rear planet carrier, the rear ring gear, and the fourth clutch C ₄ to the output shaft.

Preferably, the EVT and mechanical compound transmission modes include EVT and mechanical compound transmission 1st gear (EVT-M1), EVT and mechanical compound transmission 2 gear (EVT-M2) and EVT and mechanical compound transmission 3rd gear (EVT-M3) , the specific control method is as follows:

EVT and mechanical compound transmission 1st gear (EVT-M1): the first clutch C ₁ , the second clutch C ₂ , the third clutch C ₃ and the first brake B ₁ are engaged, while the fourth clutch C ₄ and the fifth clutch C ₅ are engaged separate from the second brake _B2 ;

The power is divided by the input shaft, and all the way through the input gear pair, the second clutch C ₂ , the electric input shaft, the inner rotor, the outer rotor, the electric output shaft, the third clutch C ₃ , the output gear pair, the output ring gear to the output planet carrier;

The other way of power passes through the first clutch C ₁ to the mechanical transmission shaft. The power is divided by the mechanical transmission shaft. One route is from the front ring gear, the front planetary carrier to the rear planetary carrier, and the other route is from the rear sun gear to the rear planetary carrier. The two routes of power converge From the rear planetary carrier, from the rear ring gear, the output sun gear to the output planetary carrier, the power of the mechanical transmission component and the electric transmission component is combined in the output planetary carrier and then output by the output shaft;

EVT and mechanical compound transmission 2nd gear (EVT-M2): the first clutch C ₁ , the second clutch C ₂ , the third clutch C ₃ and the fifth clutch C ₅ are engaged, while the fourth clutch C ₄ and the first brake B ₁ separate from the second brake _B2 ;

The power is divided by the input shaft, and all the way through the input gear pair, the second clutch C ₂ , the electric input shaft, the inner rotor, the outer rotor, the electric output shaft, the third clutch C ₃ , the output gear pair, the output ring gear to the output planet carrier;

Another way of power is from the input shaft to the mechanical transmission shaft through the first clutch _C1 , and the power is divided by the mechanical transmission shaft. The first route is the fifth clutch _C5 , the front sun gear to the front planetary carrier, and the second route is from the front ring gear to the front planets The power of the first and second roads converges to the rear planetary carrier, and the third route is routed from the rear sun gear to the rear planetary carrier. The power of the mechanical transmission assembly and the electric transmission assembly is combined in the output planet carrier and then output by the output shaft;

EVT and mechanical compound transmission 3rd gear (EVT-M3): the first clutch C ₁ , the second clutch C ₂ , the third clutch C ₃ and the second brake B ₂ are engaged, while the fourth clutch C ₄ and the fifth clutch C ₅ are engaged separate from the first brake _B1 ;

The power is divided by the input shaft, and all the way through the input gear pair, the second clutch C ₂ , the electric input shaft, the inner rotor, the outer rotor, the electric output shaft, the third clutch C ₃ , the output gear pair, the output ring gear to the output planet carrier;

Another way of power is engaged by the input shaft through the first clutch C ₁ , the fourth clutch C ₄ and the second brake B ₂ , while the second clutch C ₂ , the third clutch C ₃ , the fifth clutch C ₅ and the first brake B ₁ Separation; the power is from the input shaft through the first clutch C ₁ , the mechanical transmission shaft, the rear sun gear, the rear planetary carrier, the rear ring gear, the output sun gear to the output planetary carrier, and the power passing through the mechanical transmission assembly and the electric transmission assembly is combined in the output After the planet carrier, it is output by the output shaft.

The preferred option, the control method of the energy recovery mode is as follows:

The third clutch C ₃ , the first brake B ₁ and the second brake B ₂ are engaged, while the first clutch C ₁ , the second clutch C ₂ , the fourth clutch C ₄ and the fifth clutch C ₅ are disengaged; the braking force is provided by the output shaft Through the output planet carrier, the output ring gear, the output gear pair, the third clutch C ₃ , and the electric output shaft to the outer rotor, the outer rotor converts mechanical energy into electrical energy and transmits it to the power supply from the stator, and the power supply stores and recovers the recovered energy in the form of electrical energy.

Preferably, when EVT is driven, the power is driven by the electric input shaft to rotate the inner rotor, a part of the mechanical energy is converted into electrical energy through the slip ring and transmitted to the power supply, and the power is converted into mechanical energy through the stator and the outer rotor and output by the electric output shaft; the other part of the mechanical energy is directly passed through the stator The electromagnetic field coupling with the outer rotor is converted into mechanical energy and output by the electric output shaft.

Preferably, the calculation method of the output shaft speed in the single-flow transmission mode is as follows:

EVT transmission mode:

In the formula, n ₀ (EVT) is the output shaft speed in EVT transmission mode, n _I is the input shaft speed, i ₁ is the transmission ratio of the input gear pair, i ₂ is the transmission ratio of the output gear pair, and i _e is the electric transmission assembly transmission ratio;

Mechanical transmission 1st gear (M1):

In the formula, n _o (M1) is the output shaft speed in the first gear of the mechanical transmission, n _I is the input shaft speed, k ₁ is the planetary gear characteristic parameter of the front planetary row assembly, and k ₂ is the planetary gear characteristic parameter of the rear planetary row assembly ;

Mechanical transmission 2nd gear (M2):

n _o (M2)=n _I

In the formula, n _o (M2) is the output shaft speed when the mechanical transmission is in second gear, and n _I is the input shaft speed;

Mechanical transmission 3rd gear (M3):

In the formula, n _o (M3) is the rotational speed of the output shaft in the third gear of the mechanical transmission, n _I is the rotational speed of the input shaft, and k ₂ is the characteristic parameter of the planetary gear of the rear planetary row assembly.

As a preferred option, the calculation method of the output shaft speed of the first gear of EVT and mechanical compound transmission (EVT-M1), the second gear of EVT and mechanical compound transmission (EVT-M2) and the third gear of EVT and mechanical compound transmission (EVT-M3) is as follows :

EVT and mechanical compound transmission 1st gear (EVT-M1):

In the formula, n _o (EVT-M1) is the output shaft speed when EVT and mechanical compound transmission are in first gear, n _I is the input shaft speed, i ₁ is the transmission ratio of the input gear pair, i ₂ is the transmission ratio of the output gear pair, i _e is the transmission ratio of the electric transmission assembly, k ₁ is the characteristic parameter of the planetary gear of the front planetary row assembly, k ₂ is the characteristic parameter of the planetary gear of the rear planetary row assembly, and k ₃ is the characteristic parameter of the planetary gear of the output shaft assembly;

EVT and mechanical compound transmission 2nd gear (EVT-M2):

In the formula, n _o (EVT-M2) is the rotation speed of the output shaft when EVT and mechanical compound transmission are at the second gear, n _I is the rotation speed of the input shaft, i ₁ is the transmission ratio of the input gear pair, and i ₂ is the transmission ratio of the output gear pair, i _e is the transmission ratio of the electric transmission assembly, k ₃ is the characteristic parameter of the planetary gear of the output shaft assembly;

EVT and mechanical compound transmission 3rd gear (EVT-M3):

In the formula, n _o (EVT-M3) is the output shaft speed when EVT and mechanical compound transmission are in third gear, n _I is the input shaft speed, i ₁ is the transmission ratio of the input gear pair, and i ₂ is the transmission ratio of the output gear pair, i _e is the transmission ratio of the electric transmission assembly, k ₂ is the characteristic parameter of the planetary gear of the rear planetary row assembly, and k ₃ is the characteristic parameter of the planetary gear of the output shaft assembly.

Beneficial effects: the present invention realizes the switching of multiple modes of EVT transmission, mechanical transmission, mechanical-EVT compound transmission and energy recovery by switching the clutch assembly and the brake assembly; it can adapt to different working conditions, improve engine power utilization, and improve fuel economy It effectively reduces the shock of shifting and increases the range of speed ratio adjustment; in terms of power adjustment, the electric transmission component can effectively supplement the driving force through the energy storage, and the EVT can also recover the energy during braking and send it back In the accumulator; the power split type mechanical-EVT compound transmission system of the present invention, the mechanical-EVT parallel transmission mode set, effectively widens the speed regulation range, and can meet the requirements of large-scale linear and nonlinear stepless speed regulation .

Description of drawings

In order to more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the following will briefly introduce the drawings that need to be used in the description of the embodiments or the prior art. Obviously, the accompanying drawings in the following description are only It is an embodiment of the present invention. For those of ordinary skill in the art, other drawings can also be obtained according to the provided drawings without creative work;

Fig. 1 is a structural principle diagram of the present invention;

Fig. 2 is a schematic diagram of the power flow of the EVT transmission mode of the present invention;

Fig. 3 is a schematic diagram of the power flow of the first gear of the mechanical transmission of the present invention;

Fig. 4 is the power flow schematic diagram of the second gear of the mechanical transmission of the present invention;

Fig. 5 is a schematic diagram of the power flow of the third gear of the mechanical transmission of the present invention;

Fig. 6 is a schematic diagram of the power flow of the first gear of EVT and mechanical compound transmission of the present invention;

Fig. 7 is a schematic diagram of the power flow of the second gear of the EVT and mechanical compound transmission of the present invention;

Fig. 8 is a schematic diagram of the power flow of the third gear of the EVT and mechanical compound transmission of the present invention;

Fig. 9 is a schematic diagram of the power flow in the energy recovery mode of the present invention;

Fig. 10 is a schematic diagram of power flow in the EVT transmission mode of the present invention

Fig. 11 is a characteristic curve diagram of the relationship between the output speed and the input speed of the present invention.

Detailed ways

The following will clearly and completely describe the technical solutions in the embodiments of the present invention with reference to the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only some, not all, embodiments of the present invention. Based on the embodiments of the present invention, all other embodiments obtained by persons of ordinary skill in the art without making creative efforts belong to the protection scope of the present invention.

In describing the present invention, it is to be understood that the terms "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", The orientation or positional relationship indicated by "bottom", "inner", "outer", etc. is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying the referred device or positional relationship. Elements must have certain orientations, be constructed and operate in certain orientations, and therefore should not be construed as limitations on the invention.

In the present invention, unless otherwise clearly specified and limited, a first feature being "on" or "under" a second feature may include direct contact between the first and second features, and may also include the first and second features Not in direct contact but through another characteristic contact between them. Moreover, "above", "above" and "above" the first feature on the second feature include that the first feature is directly above and obliquely above the second feature, or simply means that the first feature is horizontally higher than the second feature. "Below", "beneath" and "under" the first feature to the second feature include that the first feature is directly below and obliquely below the second feature, or simply means that the first feature has a lower level than the second feature.

As shown in Figure 1, a compound transmission system with mechanical and electrical stepless transmission,

Including an input shaft assembly, the input shaft assembly 1 includes an input shaft 11, a first clutch C ₁ 12 and an input gear pair 13;

The mechanical transmission assembly 2, the mechanical transmission assembly 2 includes a mechanical transmission shaft 21, a front planetary row assembly 22, a rear planetary row assembly 23, a fifth clutch _C5 24, a first brake _B1 25 and a second brake _B2 26, The front planetary row assembly 22 includes a front sun gear 221, a front planetary carrier 222, and a front ring gear 223, and the rear planetary row assembly 23 includes a rear sun gear 231, a rear planetary carrier 232, and a rear ring gear 233; the mechanical transmission The shaft 21 is connected to the input shaft 11 through the first clutch C ₁ 12, the mechanical transmission shaft 21 is fixedly connected to the front ring gear 223 and the rear sun gear 231 respectively, the front planetary carrier 222 is connected to the rear planetary carrier 232, and the The front sun gear 221 is connected with the mechanical transmission shaft 21 through the fifth clutch C ₅ 24, the first brake B ₁ 25 can lock the front sun gear 221, and the second brake B ₂ 26 can lock the front planetary carrier 222 and the rear planetary carrier 222 simultaneously. Planet carrier 232;

An electric transmission assembly 3, the electric transmission assembly 3 includes an electric input shaft 31, an inner rotor 32, an outer rotor 33, a stator 34, a power supply 35, an electric output shaft 36, a second clutch C ₂ 37 and a third clutch C ₃ 38; The input gear pair 13 is connected to the electric input shaft 31 through the second clutch C ₂ 37, the electric input shaft 31 is connected to the inner rotor 32, the electric output shaft 36 is connected to the outer rotor 33, and the power supply 35 is given to the stator 34 supplies power to generate a magnetic field, and the magnetic field generated by the stator 34 controls the transmission speed ratio of the inner rotor 32 relative to the outer rotor 33 to realize the adjustment of the transmission speed ratio of the electric input shaft 31 relative to the electric output shaft 36;

The output shaft assembly 4, the output shaft assembly 4 includes the output shaft 41, the output sun gear 42, the output planet carrier 43, the output ring gear 44, the output gear pair 45 and the fourth clutch C ₄ 46; the output sun gear 42 and The rear ring gear 233 is connected, the output ring gear 44 is connected to the third clutch _C338 through the output gear pair 45, the output planet carrier 43 is connected to the output shaft 41, and the output sun gear 42 is connected to the fourth clutch _C4 46 is connected with the output shaft 41.

The present invention realizes the switching of multiple modes of EVT transmission, mechanical transmission, mechanical-EVT compound transmission and energy recovery by switching the clutch assembly and the brake assembly; it can adapt to different working conditions, improve engine power utilization, and improve fuel economy; effectively The impact of shifting is greatly reduced, and the range of speed ratio adjustment is increased; in terms of power adjustment, the electric transmission component can effectively supplement the driving force through the energy storage, and the EVT can also recover the energy during braking and send it back to the energy storage. Middle: The power-split mechanical-EVT compound transmission system of the present invention has a mechanical-EVT parallel transmission mode, which effectively broadens the speed regulation range and can meet the requirements of large-scale linear and nonlinear stepless speed regulation.

In order to recover the braking energy and supplement the driving power at the same time, the electric transmission assembly 3 includes a slip ring 39, the slip ring 39 is connected with the inner rotor 32, and the inner rotor 32 converts mechanical energy into electrical energy, and the generated electrical energy passes through The slip ring 39 feeds the power supply 35 .

A control method for a mechanically and electrically continuously variable compound transmission system, which realizes switching between a single-flow transmission mode, a compound transmission mode and an energy recovery mode through combined switching between a clutch and a brake; the single-flow transmission mode includes EVT transmission mode and mechanical transmission mode; the compound transmission mode is EVT and mechanical compound transmission mode.

The engagement elements of each transmission mode are shown in Table 1. details as follows:

Table 1 Mode switching element engagement state

Note: ▲ means the actuator is in the engaged state, △ means the actuator is in the disengaged state.

As shown in Figure 2, the control method of the EVT transmission mode is as follows:

Second clutch _C2 37 , third clutch _C3 38 and fourth clutch _C4 46 are engaged while first clutch _C1 12 , fifth clutch _C5 24 , first brake _B1 25 and second brake _B2 26 Separation; power passes through the input shaft 11 through the input gear pair 13, the second clutch C ₂ 37, the electric input shaft 31, the inner rotor 32, the outer rotor 33, the electric output shaft 36, the third clutch C ₃ 38, the output gear pair 45, The output ring gear 44 and the output planet carrier 43 are output to the output shaft 41 .

The calculation method of the rotating speed of the output shaft 41 in the EVT transmission mode is as follows:

In the formula, n ₀ (EVT) is the rotational speed of the output shaft 41 under the EVT transmission mode, n _I is the rotational speed of the input shaft 11, i ₁ is the transmission ratio of the input gear pair 13, i ₂ is the transmission ratio of the output gear pair 45, i _e is the transmission ratio of the electric transmission assembly 3.

As shown in Figure 3, the control method of the first gear (M1) of the mechanical transmission is as follows:

First clutch C ₁ 12 , fourth clutch C ₄ 46 and first brake B ₁ 25 are engaged while second clutch C ₂ 37 , third clutch C ₃ 38 , fifth clutch C ₅ 24 and second brake B ₂ 26 Separation; the power is from the input shaft 11 to the mechanical transmission shaft 21 through the first clutch C ₁ 12, and the power is divided by the mechanical transmission shaft 21, one route is the front ring gear 223, the front planetary carrier 222 to the rear planetary carrier 232, and the other route is the rear sun wheel 231 to the rear planetary carrier 232, the two-way power converges on the rear planetary carrier 232, and then is output from the rear ring gear 233, the fourth clutch _C446 to the output shaft 41;

The calculation method of the rotational speed of the output shaft 41 of the first gear (M1) of the mechanical transmission is as follows:

In the formula, n _o (M1) is the rotational speed of the output shaft 41 during the first gear of the mechanical transmission, n _I is the rotational speed of the input shaft 11, k ₁ is the planetary gear characteristic parameter of the front planetary row assembly 22, and k ₂ is the speed of the rear planetary row assembly 23 Planetary gear characteristic parameters.

As shown in Figure 4, the control method of the second gear (M2) of the mechanical transmission is as follows:

First clutch C ₁ 12 , fourth clutch C ₄ 46 and fifth clutch C ₅ 24 are engaged while second clutch C ₂ 37 , third clutch C ₃ 38 , first brake B ₁ 25 and second brake B ₂ 26 Separation; the power is from the input shaft 11 to the mechanical transmission shaft 21 through the first clutch C ₁ 12, the power is divided by the mechanical transmission shaft 21, the first route is the fifth clutch C ₅ 24, the front sun gear 221 to the front planetary carrier 222, the second The front ring gear 223 is routed to the front planetary carrier 222, the power of the first road and the second road are merged to the rear planetary carrier 232, and the third route is routed from the rear sun gear 231 to the rear planetary carrier 232, and the power is merged in the rear planetary carrier 232, and then by The rear ring gear 233, the fourth clutch C ₄ 46 are output to the output shaft 41;

The calculation method of the rotating speed of the output shaft 41 of the second gear (M2) of the mechanical transmission is as follows:

n _o (M2)=n _I

In the formula, n _o (M2) is the rotational speed of the output shaft 41 when the mechanical transmission is in the second gear, and n _I is the rotational speed of the input shaft 11.

As shown in Figure 5, the control method of the third gear (M3) of the mechanical transmission is as follows:

First clutch C ₁ 12 , fourth clutch C ₄ 46 and second brake B ₂ 26 are engaged while second clutch C ₂ 37 , third clutch C ₃ 38 , fifth clutch C ₅ 24 and first brake B ₁ 25 Separation; power is output from the input shaft 11 through the first clutch C ₁ 12 , the mechanical transmission shaft 21 , the rear sun gear 231 , the rear planet carrier 232 , the rear ring gear 233 , and the fourth clutch C ₄ 46 to the output shaft 41 .

The calculation method of the rotational speed of the output shaft 41 of the mechanical transmission 3rd gear (M3) is as follows:

In the formula, n _o (M3) is the rotation speed of the output shaft 41 in the third gear of the mechanical transmission, n _I is the rotation speed of the input shaft 11, and k ₂ is the characteristic parameter of the planetary gear of the rear planetary row assembly 23.

As shown in Figure 6, the control method of EVT and first gear of mechanical compound transmission (EVT-M1) is as follows:

First clutch C ₁ 12 , second clutch C ₂ 37 , third clutch C ₃ 38 and first brake B ₁ 25 are engaged while fourth clutch C ₄ 46 , fifth clutch C ₅ 24 and second brake B ₂ 26 separation;

The power is divided by the input shaft 11, all the way through the input gear pair 13, the second clutch C ₂ 37, the electric input shaft 31, the inner rotor 32, the outer rotor 33, the electric output shaft 36, the third clutch C ₃ 38, and the output gear pair 45 , the output ring gear 44 to the output planet carrier 43;

Another way of power passes through the first clutch C ₁ 12 to the mechanical transmission shaft 21, the power is divided by the mechanical transmission shaft 21, one route is from the front ring gear 223, the front planetary carrier 222 to the rear planetary carrier 232, and the other route is from the rear sun gear 231 to the rear The planetary carrier 232, the two-way power converges on the rear planetary carrier 232, and then from the rear ring gear 233, the output sun gear 42 to the output planetary carrier 43, the power passing through the mechanical transmission assembly 2 and the electric transmission assembly 3 merges after the output planetary carrier 43 output by the output shaft 41.

The calculation method for the rotational speed of the output shaft 41 of EVT and mechanical compound transmission first gear (EVT-M1) is as follows:

In the formula, n _o (EVT-M1) is the rotation speed of the output shaft 41 when the EVT and the mechanical compound transmission are in gear 1, n _I is the rotation speed of the input shaft 11, i ₁ is the transmission ratio of the input gear pair 13, and i ₂ is the output gear pair 45 transmission ratio, i _e is the transmission ratio of the electric transmission assembly 3, k ₁ is the planetary gear characteristic parameter of the front planetary row assembly 22, k ₂ is the planetary gear characteristic parameter of the rear planetary row assembly 23, and k ₃ is the output shaft assembly 4 The characteristic parameters of the planetary gear.

As shown in Figure 7, the control method of EVT and mechanical compound transmission 2nd gear (EVT-M2) is as follows:

First clutch C ₁ 12 , second clutch C ₂ 37 , third clutch C ₃ 38 and fifth clutch C ₅ 24 are engaged while fourth clutch C ₄ 46 , first brake B ₁ 25 and second brake B ₂ 26 separation;

The power is divided by the input shaft 11, all the way through the input gear pair 13, the second clutch C ₂ 37, the electric input shaft 31, the inner rotor 32, the outer rotor 33, the electric output shaft 36, the third clutch C ₃ 38, and the output gear pair 45 , the output ring gear 44 to the output planet carrier 43;

Another way of power is from the input shaft 11 to the mechanical transmission shaft 21 through the first clutch _C112 , and the power is divided by the mechanical transmission shaft 21. The first route is the fifth clutch _C524 , the front sun gear 221 to the front planetary carrier 222, and the second The front ring gear 223 is routed to the front planetary carrier 222, the power of the first road and the second road are merged to the rear planetary carrier 232, and the third route is routed from the rear sun gear 231 to the rear planetary carrier 232, and the power is merged in the rear planetary carrier 232, and then by The rear ring gear 233 , the output sun gear 42 to the output planet carrier 43 , the power of the mechanical transmission assembly 2 and the electric transmission assembly 3 converges on the output planet carrier 43 and then is output by the output shaft 41 ;

The calculation method for the rotational speed of the output shaft 41 of EVT and mechanical compound transmission 2nd gear (EVT-M2) is as follows:

In the formula, n _o (EVT-M2) is the rotation speed of the output shaft 41 when the EVT and mechanical compound transmission are at the second gear, n _I is the rotation speed of the input shaft 11, i ₁ is the transmission ratio of the input gear pair 13, and i ₂ is the output gear pair 45 The transmission ratio, _ie is the transmission ratio of the electric transmission assembly 3, and k ₃ is the characteristic parameter of the planetary gear of the output shaft assembly 4.

As shown in Figure 8, the control method of EVT and mechanical compound transmission 3rd gear (EVT-M3) is as follows:

First clutch C ₁ 12 , second clutch C ₂ 37 , third clutch C ₃ 38 and second brake B ₂ 26 are engaged while fourth clutch C ₄ 46 , fifth clutch C ₅ 24 and first brake B ₁ 25 separation;

The power is divided by the input shaft 11, all the way through the input gear pair 13, the second clutch C ₂ 37, the electric input shaft 31, the inner rotor 32, the outer rotor 33, the electric output shaft 36, the third clutch C ₃ 38, and the output gear pair 45 , the output ring gear 44 to the output planet carrier 43;

Another way of power is engaged by the input shaft 11 through the first clutch C ₁ 12, the fourth clutch C ₄ 46 and the second brake B ₂ 26, while the second clutch C ₂ 37, the third clutch C ₃ 38, and the fifth clutch C ₅ 24 and the first brake B ₁ 25 are separated; the power is from the input shaft 11 through the first clutch C ₁ 12, the mechanical transmission shaft 21, the rear sun gear 231, the rear planet carrier 232, the rear ring gear 233, the output sun gear 42 to the output planet The power of the carrier 43 after passing through the mechanical transmission assembly 2 and the electric transmission assembly 3 is combined in the output planetary carrier 43 and then output by the output shaft 41 .

The calculation method for the rotational speed of the output shaft 41 of EVT and mechanical compound transmission 3rd gear (EVT-M3) is as follows:

In the formula, n _o (EVT-M3) is the rotation speed of the output shaft 41 when the EVT and mechanical compound transmission are in third gear, n _I is the rotation speed of the input shaft 11, i ₁ is the transmission ratio of the input gear pair 13, and i ₂ is the output gear pair 45 The transmission ratio, ie _is the transmission ratio of the electric transmission assembly 3, k ₂ is the planetary gear characteristic parameter of the rear planetary row assembly 23, and k ₃ is the planetary gear characteristic parameter of the output shaft assembly 4.

As shown in Figure 9, the control method of the energy recovery mode is as follows:

Third clutch C ₃ 38 , first brake B ₁ 25 and second brake B ₂ 26 are engaged while first clutch C ₁ 12 , second clutch C ₂ 37 , fourth clutch C ₄ 46 and fifth clutch C ₅ 24 Separation; the braking force is from the output shaft 41 to the outer rotor 33 through the output planet carrier 43, the output ring gear 44, the output gear pair 45, the third clutch C ₃ 38, the electric output shaft 36, and the outer rotor 33 converts mechanical energy into electrical energy by the stator 34 to a power source 35 which stores the recovered energy in the form of electrical energy.

As shown in Figure 10, during EVT transmission, the power is driven by the electric input shaft 31 to rotate the inner rotor 32, a part of the mechanical energy is converted into electrical energy through the slip ring 39 and transmitted to the power supply 35, and the power supply 35 is converted into mechanical energy by the electric motor through the stator 34 and the outer rotor 33. The output shaft 36 is output; another part of mechanical energy is directly converted into mechanical energy by the electromagnetic field coupling between the stator 34 and the outer rotor 33 and output by the electric output shaft 36 .

EVT transmissions, EVT-M1 compound transmissions, EVT-M2 compound transmissions and EVT-M3 compound transmissions are provided by adjusting the gear ratios of the EVT transmission assemblies and selectively controlling the engagement of said clutch assemblies and brake assemblies, as shown in Figure 11. a transmission method. When starting in EVT transmission mode, the output speed increases linearly with the increase of the transmission ratio i _e of the EVT transmission assembly; when the transmission ratio i _e ∈[n _o (EVT)=n _o (EVT-M3)] of the EVT transmission assembly, The EVT transmission mode can be switched to the EVT-M3 compound transmission mode synchronously. When the transmission ratio of the EVT transmission assembly changes from the minimum value to the maximum value, n _o (EVT-M3) increases non-linearly; the EVT-M2 transmission mode is used to start the output speed The output speed increases nonlinearly with the increase of the transmission ratio i _e of the EVT transmission assembly; when using the EVT-M2 transmission mode, the output speed increases non-linearly with the increase of the transmission ratio i _e of the EVT transmission assembly. By selectively controlling the engagement of the clutch assembly and the brake assembly, three transmission modes of mechanical transmission M1, M2 and M3 are provided, and three different fixed-ratio mechanical transmission modes can be obtained.

for example:

The main parameters are: i ₁ =0.51, i ₂ =0.5, k ₁ =1.86, k ₂ =1.5, k ₃ =1.72, i _e ∈[0,3.5]

The relationship between EVT transmission output-input speed is:

The output-input speed relationship of mechanical transmission M1 is:

The output-input speed relationship of mechanical transmission M2 is: n _o (M2) = n _I

The output-input speed relationship of mechanical transmission M3 is:

The relationship between EVT-mechanical compound transmission EVT-M1 output-input speed is:

The relationship between EVT-mechanical compound transmission EVT-M1 output-input speed is:

The relationship between EVT-mechanical compound transmission EVT-M1 output-input speed is:

As shown in Figure 11, using the EVT transmission mode to start, when the transmission ratio i _e of the EVT transmission mechanism changes from 0 to 3.5, n _o (EVT) increases linearly from 0 to 3.43n _I ; when the transmission ratio of the EVT transmission mechanism When i _e = 2.4, the EVT transmission mode can be switched to the EVT-mechanical compound transmission EVT-M3 mode synchronously, and the EVT-mechanical compound transmission EVT-M3 mode is a nonlinear transmission; the EVT-mechanical compound transmission EVT-M2 mode is used to start. mode, when the transmission ratio i _e of the EVT transmission mechanism changes from 0 to 3.5, n _o increases nonlinearly from 0 to 0.86n _I ; in the EVT-mechanical compound transmission EVT-M1 mode, when the transmission ratio i of the EVT transmission mechanism _{As e} varies from 0 to 3.5, n _o increases linearly from 2.68n _I to 4.19n _I. By selectively controlling the engagement of the clutch assembly and the brake assembly, three transmission modes of mechanical transmission M1, M2, and M3 are provided, and three different fixed-ratio mechanical transmission modes can be obtained, respectively n _o (M1)=1.08n _I , n _o (M2) = 1n _I and n _o (M3) = 0.67n _I .

Each embodiment in this specification is described in a progressive manner, each embodiment focuses on the difference from other embodiments, and the same and similar parts of each embodiment can be referred to each other. As for the device disclosed in the embodiment, since it corresponds to the method disclosed in the embodiment, the description is relatively simple, and for relevant details, please refer to the description of the method part.

The above description of the disclosed embodiments is provided to enable any person skilled in the art to make or use the invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of the invention. Therefore, the present invention will not be limited to the embodiments shown herein, but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.

Claims (10)

1. A compound transmission system with mechanical and electrical stepless speed change, characterized in that:

   An input shaft assembly (1) is included, and the input shaft assembly (1) includes an input shaft (11), a first clutch C ₁ (12) and an input gear pair (13);

   A mechanical transmission assembly (2), the mechanical transmission assembly (2) comprising a mechanical transmission shaft (21), a front planetary row assembly (22), a rear planetary row assembly (23), a fifth clutch _C5 (24), a first Brake B ₁ (25) and second brake B ₂ (26), the front planetary row assembly (22) includes a front sun gear (221), a front planet carrier (222), a front ring gear (223), and the rear The planetary row assembly (23) includes a rear sun gear (231), a rear planetary carrier (232) and a rear ring gear (233); the mechanical transmission shaft ( ₂₁ ) is connected to the input shaft (11 ) connection, the mechanical transmission shaft (21) is fixedly connected with the front ring gear (223) and the rear sun gear (231) respectively, the front planet carrier (222) is connected with the rear planet carrier (232), and the front sun gear The wheel (221) is connected with the mechanical transmission shaft (21) through the fifth clutch C ₅ (24), the first brake B ₁ (25) can lock the front sun gear (221), and the second brake B ₂ (26 ) can simultaneously lock the front planet carrier (222) and the rear planet carrier (232);

   An electric transmission assembly (3), the electric transmission assembly (3) comprising an electric input shaft (31), an inner rotor (32), an outer rotor (33), a stator (34), a power supply (35), an electric output shaft (36 ), the second clutch C ₂ (37) and the third clutch C ₃ (38); the input gear pair (13) is connected with the electric input shaft (31) through the second clutch C ₂ (37), and the electric input The shaft (31) is connected to the inner rotor (32), the electric output shaft (36) is connected to the outer rotor (33), the power supply (35) supplies power to the stator (34) to generate a magnetic field, and the stator (34) generates The magnetic field controls the transmission speed ratio of the inner rotor (32) relative to the outer rotor (33), and realizes the adjustment of the transmission speed ratio of the electric input shaft (31) relative to the electric output shaft (36);

   The output shaft assembly (4), the output shaft assembly (4) includes an output shaft (41), an output sun gear (42), an output planet carrier (43), an output ring gear (44), an output gear pair (45) and The fourth clutch C ₄ (46); the output sun gear (42) is connected to the rear ring gear (233), and the output ring gear (44) is connected to the third clutch C ₃ (38) through the output gear pair (45) connected, the output planet carrier (43) is connected to the output shaft (41), and the output sun gear (42) is connected to the output shaft (41) through the fourth clutch C ₄ (46).
2. The mechanical and electrical continuously variable compound transmission system according to claim 1, characterized in that: the electric transmission assembly (3) includes a slip ring (39), and the slip ring (39) is connected to the inner rotor (32) connected, the inner rotor (32) converts mechanical energy into electrical energy, and the generated electrical energy is delivered to the power supply (35) through the slip ring (39).
3. According to the control method of the compound transmission system of mechanical and electrical continuously variable speed change according to claim 1 or 2, it is characterized in that: through the combined switching between the clutch and the brake, the single-flow transmission mode, the compound transmission mode and the energy recovery mode are realized. switching; the single-stream transmission mode includes EVT transmission mode and mechanical transmission mode; the compound transmission mode is EVT and mechanical compound transmission mode.
4. According to the control method of the compound transmission system of mechanical and electrical continuously variable speed change according to claim 3, it is characterized in that, the control method of the EVT transmission mode is as follows:

   Second clutch C ₂ (37), third clutch C ₃ (38) and fourth clutch C ₄ (46) are engaged while first clutch C ₁ (12), fifth clutch C ₅ (24), first brake B ₁ (25) is separated from the second brake B ₂ (26); the power is from the input shaft (11) through the input gear pair (13), the second clutch C ₂ (37), the electric input shaft (31), the inner rotor ( 32), outer rotor (33), electric output shaft (36), third clutch C ₃ (38), output gear pair (45), output ring gear (44), output planet carrier (43) to output shaft (41 ) output.
5. According to the control method of the compound transmission system of mechanical and electrical continuously variable speed change according to claim 3, it is characterized in that the mechanical transmission mode includes the first gear of mechanical transmission, the second gear of mechanical transmission and the third gear of mechanical transmission, and the specific control method is as follows :

   Mechanical transmission 1st gear (M1): the first clutch C ₁ (12), the fourth clutch C ₄ (46) and the first brake B ₁ (25) are engaged, while the second clutch C ₂ (37), the third clutch C ₃ (38), the fifth clutch C ₅ (24) and the second brake B ₂ (26) are separated; the power is from the input shaft (11) to the mechanical transmission shaft (21) through the first clutch C ₁ (12), and the power is from The mechanical transmission shaft (21) splits, one route is from the front ring gear (223), the front planetary carrier (222) to the rear planetary carrier (232), and the other route is from the rear sun gear (231) to the rear planetary carrier (232), two routes The power is combined in the rear planetary carrier (232), and then output from the rear ring gear (233), the fourth clutch _C4 (46) to the output shaft (41);

   Mechanical transmission 2nd gear (M2): the first clutch C ₁ (12), the fourth clutch C ₄ (46) and the fifth clutch C ₅ (24) are engaged, while the second clutch C ₂ (37), the third clutch C ₃ (38), the first brake B ₁ (25) and the second brake B ₂ (26) are separated; the power is from the input shaft (11) to the mechanical transmission shaft (21) through the first clutch C ₁ (12), and the power is from The mechanical transmission shaft (21) splits, the first route is the fifth clutch _C5 (24), the front sun gear (221) to the front planetary carrier (222), the second route is the front ring gear (223) to the front planetary carrier (222) , the first road and the second road power merge to the rear planetary carrier (232), the third route is from the rear sun gear (231) to the rear planetary carrier (232), the power is merged in the rear planetary circle (233), the fourth clutch C ₄ (46) to the output shaft (41) output;

   Mechanical transmission 3rd gear (M3): the first clutch C ₁ (12), the fourth clutch C ₄ (46) and the second brake B ₂ (26) are engaged, while the second clutch C ₂ (37), the third clutch C ₃ (38), the fifth clutch C ₅ (24) and the first brake B ₁ (25) are separated; the power is passed by the input shaft (11) through the first clutch C ₁ (12), the mechanical transmission shaft (21), the rear sun wheel (231), rear planetary carrier (232), rear ring gear (233), fourth clutch C ₄ (46) to the output shaft (41) for output.
6. According to the control method of the compound transmission system of mechanical and electrical continuously variable speed change according to claim 3, it is characterized in that, the EVT and mechanical compound transmission mode includes EVT and mechanical compound transmission 1 gear (EVT-M1), EVT and mechanical 2nd gear of compound transmission (EVT-M2) and 3rd gear of EVT and mechanical compound transmission (EVT-M3), the specific control method is as follows:

   EVT and mechanical compound transmission 1st gear (EVT-M1): the first clutch C ₁ (12), the second clutch C ₂ (37), the third clutch C ₃ (38) and the first brake B ₁ (25), Simultaneously, the fourth clutch C ₄ (46), the fifth clutch C ₅ (24) and the second brake B ₂ (26) are disengaged;

   The power is split by the input shaft (11), and passes through the input gear pair (13), the second clutch C ₂ (37), the electric input shaft (31), the inner rotor (32), the outer rotor (33), the electric output shaft ( 36), the third clutch C ₃ (38), the output gear pair (45), the output ring gear (44) to the output planet carrier (43);

   Another way of power passes through the first clutch C ₁ (12) to the mechanical transmission shaft (21), the power is divided by the mechanical transmission shaft (21), and one route is from the front ring gear (223), the front planetary carrier (222) to the rear planetary carrier ( 232), the other is routed from the rear sun gear (231) to the rear planetary carrier (232), the two-way power converges on the rear planetary carrier (232), and then from the rear ring gear (233), the output sun gear (42) to the output planet The frame (43), after the power of the mechanical transmission assembly (2) and the electric transmission assembly (3), is merged in the output planetary carrier (43), it is output by the output shaft (41);

   EVT and mechanical compound transmission 2nd gear (EVT-M2): the first clutch C ₁ (12), the second clutch C ₂ (37), the third clutch C ₃ (38) and the fifth clutch C ₅ (24), At the same time, the fourth clutch C ₄ (46), the first brake B ₁ (25) and the second brake B ₂ (26) are disengaged;

   The power is split by the input shaft (11), and passes through the input gear pair (13), the second clutch C ₂ (37), the electric input shaft (31), the inner rotor (32), the outer rotor (33), the electric output shaft ( 36), the third clutch C ₃ (38), the output gear pair (45), the output ring gear (44) to the output planet carrier (43);

   Another way of power is from the input shaft (11) to the mechanical transmission shaft (21) through the first clutch C ₁ (12), the power is divided by the mechanical transmission shaft (21), the first route is the fifth clutch C ₅ (24), the front sun wheel (221) to the front planetary carrier (222), the second route is from the front ring gear (223) to the front planetary carrier (222), the power of the first route and the second route is merged to the rear planetary carrier (232), and the third route From the rear sun gear (231) to the rear planet carrier (232), the power converges on the rear planet carrier (232), and then from the rear ring gear (233), the output sun gear (42) to the output planet carrier (43), through mechanical transmission The power of the component (2) and the electric transmission component (3) is combined in the output planet carrier (43) and then output by the output shaft (41);

   EVT and mechanical compound transmission 3rd gear (EVT-M3): the first clutch C ₁ (12), the second clutch C ₂ (37), the third clutch C ₃ (38) and the second brake B ₂ (26), Simultaneously, the fourth clutch C ₄ (46), the fifth clutch C ₅ (24) and the first brake B ₁ (25) are separated;

   The power is split by the input shaft (11), and passes through the input gear pair (13), the second clutch C ₂ (37), the electric input shaft (31), the inner rotor (32), the outer rotor (33), the electric output shaft ( 36), the third clutch C ₃ (38), the output gear pair (45), the output ring gear (44) to the output planet carrier (43);

   Another way of power is engaged by the input shaft (11) through the first clutch C ₁ (12), the fourth clutch C ₄ (46) and the second brake B ₂ (26), while the second clutch C ₂ (37), the third Clutch C ₃ (38), fifth clutch C ₅ (24) and first brake B ₁ (25) are separated; power is passed through first clutch C ₁ (12), mechanical drive shaft (21), Rear sun gear (231), rear planetary carrier (232), rear ring gear (233), output sun gear (42) to output planetary carrier (43), through mechanical transmission assembly (2) and electric transmission assembly (3) The power is output by the output shaft (41) after being merged in the output planet carrier (43).
7. According to the control method of the compound transmission system of mechanical and electrical continuously variable speed change according to claim 3, it is characterized in that the control method of the energy recovery mode is as follows:

   The third clutch C ₃ (38), the first brake B ₁ (25) and the second brake B ₂ (26) are engaged, while the first clutch C ₁ (12), the second clutch C ₂ (37), the fourth clutch C ₄ (46) is separated from the fifth clutch C ₅ (24); the braking force is transmitted from the output shaft (41) through the output planet carrier (43), the output ring gear (44), the output gear pair (45), the third clutch C ₃ (38), the electric output shaft (36) to the outer rotor (33), the outer rotor (33) converts mechanical energy into electrical energy and transmits it from the stator (34) to the power supply (35), and the power supply (35) stores and recycles it in the form of electrical energy energy.
8. According to claim 4 or 6, the control method of the compound transmission system of mechanical and electrical stepless speed change is characterized in that: when EVT transmission, the power is driven by the electric input shaft (31) to rotate the inner rotor (32), and a part of the mechanical energy passes through The slip ring (39) is converted into electrical energy and transmitted to the power supply (35), and the power supply (35) is converted into mechanical energy by the stator (34) and the outer rotor (33) and output by the electric output shaft (36); another part of the mechanical energy is directly passed through the stator (34) ) and the electromagnetic field coupling between the outer rotor (33) is converted into mechanical energy and output by the electric output shaft (36).
9. According to the control method of the compound transmission system of mechanical and electrical stepless speed change according to claim 4 or 5, it is characterized in that, the calculation method of the rotational speed of the output shaft (41) in the single-flow transmission mode is as follows:

   EVT transmission mode:

   

   In the formula, n ₀ (EVT) is the rotating speed of the output shaft (41) under the EVT transmission mode, n _I is the rotating speed of the input shaft (11), i ₁ is the transmission ratio of the input gear pair (13), and i ₂ is the output gear pair ( 45) transmission ratio, i _e is the transmission ratio of the electric drive assembly (3);

   Mechanical transmission 1st gear (M1):

   

   In the formula, n _o (M1) is the rotational speed of the output shaft (41) at the first gear of the mechanical transmission, n _I is the rotational speed of the input shaft (11), k ₁ is the planetary gear characteristic parameter of the front planetary row assembly (22), and k ₂ is The planetary gear characteristic parameters of the rear planetary row assembly (23);

   Mechanical transmission 2nd gear (M2):

   n _o (M2)=n _I

   In the formula, n _o (M2) is output shaft (41) rotating speed when mechanical transmission 2 gears, and n _I is input shaft (11) rotating speed;

   Mechanical transmission 3rd gear (M3):

   

   In the formula, n _o (M3) is the rotational speed of the output shaft (41) when the mechanical transmission is in third gear, n _I is the rotational speed of the input shaft (11) and k ₂ is the characteristic parameter of the planetary gear of the rear planetary row assembly (23).
10. The control method of the compound transmission system of mechanical and electrical stepless speed change according to claim 6, characterized in that, the first gear (EVT-M1) of the EVT and mechanical compound transmission, the second gear (EVT-M1) of the EVT and mechanical compound transmission (EVT- M2) and the output shaft (41) speed calculation method of EVT and mechanical compound transmission 3rd gear (EVT-M3) is as follows:

    EVT and mechanical compound transmission 1st gear (EVT-M1):

    

    In the formula, n _o (EVT-M1) is the rotation speed of the output shaft (41) when the EVT and mechanical compound transmission are in first gear, n _I is the rotation speed of the input shaft (11), i ₁ is the transmission ratio of the input gear pair (13), and i ₂ is the transmission ratio of the output gear pair (45), i _e is the transmission ratio of the electric transmission assembly (3), k ₁ is the planetary gear characteristic parameter of the front planetary row assembly (22), k ₂ is the rear planetary row assembly (23 ) planetary gear characteristic parameter, k ₃ is the planetary gear characteristic parameter of output shaft assembly (4);

    EVT and mechanical compound transmission 2nd gear (EVT-M2):

    

    In the formula, n _o (EVT-M2) is the rotation speed of the output shaft (41) when the EVT and mechanical compound transmission are in second gear, n _I is the rotation speed of the input shaft (11), i ₁ is the transmission ratio of the input gear pair (13), and i ₂ is the transmission ratio of the output gear pair (45), i _e is the transmission ratio of the electric transmission assembly (3), and k ₃ is the planetary gear characteristic parameter of the output shaft assembly (4);

    EVT and mechanical compound transmission 3rd gear (EVT-M3):

    

    In the formula, n _o (EVT-M3) is the rotation speed of the output shaft (41) when EVT and mechanical compound transmission are in third gear, n _I is the rotation speed of the input shaft (11), i ₁ is the transmission ratio of the input gear pair (13), and i ₂ is the transmission ratio of the output gear pair (45), i _e is the transmission ratio of the electric transmission assembly (3), k ₂ is the planetary gear characteristic parameter of the rear planetary row assembly (23), and k ₃ is the output shaft assembly (4) The characteristic parameters of the planetary gear.

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