CN213108992U

CN213108992U - Multi-gear double-motor driving system and vehicle

Info

Publication number: CN213108992U
Application number: CN202021967374.8U
Authority: CN
Inventors: 邢杰; 段志辉; 杨良会; 杨上东; 徐东博; 赵迁; 王站影; 马永志; 原诚寅
Original assignee: Beijing New Energy Vehicle Technology Innovation Center Co Ltd
Current assignee: Beijing New Energy Vehicle Technology Innovation Center Co Ltd
Priority date: 2020-09-10
Filing date: 2020-09-10
Publication date: 2021-05-04
Anticipated expiration: 2030-09-10

Abstract

The utility model relates to the technical field of automobile power drive, in particular to a multi-gear dual-motor drive system and a vehicle, wherein the system comprises a first motor, a second motor, a power coupling mechanism and a dual-shaft gear box; the double-shaft gearbox comprises a gear shifting mechanism, a first input shaft and a second input shaft; the power coupling mechanism comprises a planetary gear set and a first clutch, the first motor and the second motor are in transmission connection with the planetary gear set respectively, and the first clutch controls the transmission relation between the planetary gear set and the first input shaft as well as between the planetary gear set and the second input shaft; the utility model can realize the unpowered interrupted gear shifting through the matching of the first motor, the second motor, the power coupling mechanism and the double-shaft gear box; multiple gear combinations of the double motors are formed, the speed ratio change range is widened, the double motors can operate in a high-efficiency interval under full speed ranges under different working conditions, and the fault tolerance and the reliability of the vehicle are improved.

Description

Multi-gear double-motor driving system and vehicle

Technical Field

The utility model relates to an automotive power drives technical field, concretely relates to two motor drive systems of many grades and vehicle.

Background

With the increasingly prominent environmental and energy safety problems, the global automobile industry has established an electrification development trend, and pure electric vehicles develop rapidly. At present, the commercial power system scheme of the pure electric vehicle mainly comprises a single-motor and speed reducer scheme and a single-motor and two-gear transmission scheme. Both schemes fail to balance the vehicle dynamics and economy requirements at full speed and full operating conditions.

The existing electric automobile electric drive system mainly adopts a single-motor single-gear structure, and the structure cannot enable a motor to operate in a high-efficiency interval in a full-speed range and cannot balance the requirements on dynamic property and economy. Electric drive multi-gear is the development trend of an electric drive system, and more single-motor multi-gear electric drive systems are applied. However, the single-motor multi-gear structure has the problem of power interruption during gear shifting, or a complex clutch hydraulic gear shifting system is adopted, so that the cost is increased, and the reliability is reduced. Moreover, the single-motor multi-gear structure is only suitable for passenger vehicles, and a single-motor system cannot work in a high-efficiency area under different working conditions when the commercial vehicle is in a no-load working condition and a full-load working condition and has a large quality difference.

SUMMERY OF THE UTILITY MODEL

In order to overcome the defects of the prior art, the technical problem to be solved by the utility model is to provide a driving system which solves the problem that the current driving system is not efficient enough and can not make the motor operate in a high-efficiency range in a full-working condition and full-speed range, and simultaneously improves the power performances of gear shifting quality, acceleration, climbing and the like; and meanwhile, the multi-gear double-motor driving system provides power redundancy for the vehicle, and improves the fault tolerance and reliability of the vehicle.

In order to solve the technical problem, the utility model discloses a technical scheme be:

a multi-gear dual-motor driving system comprises a first motor, a second motor, a power coupling mechanism and a dual-shaft gear box;

the double-shaft gearbox comprises a gear shifting mechanism, a first input shaft, a second input shaft and an output shaft, wherein odd gears are arranged on the first input shaft, even gears are arranged on the second input shaft, and the gear shifting mechanism controls the output shaft to be in transmission connection with the first input shaft and the second input shaft;

the power coupling mechanism comprises a planetary gear set and a first clutch, the first motor and the second motor are in transmission connection with the planetary gear set respectively, and the first clutch controls the transmission relation between the planetary gear set and the first input shaft as well as between the planetary gear set and the second input shaft;

when the first clutch is closed, the gear shifting mechanism is engaged into any gear;

when the first clutch is separated, the gear shifting mechanism is used for selecting and engaging an odd gear and an even gear.

Preferably, the planetary gear set comprises three transmission elements, and the transmission elements are a first sun gear, a first ring gear and a first planet carrier;

one of the transmission elements is connected with the first motor,

the remaining one of the transmission elements is connected to the first input shaft,

the rest one transmission element is connected with the second input shaft and the second motor;

and a first clutch is arranged between any two of the three transmission elements.

Preferably, the planetary gear set is a compound planetary gear.

Preferably, the compound planetary gear is a ravigneaux planetary gear;

the Lavenner planetary gear comprises four transmission elements, and the transmission elements are a second sun gear, a second planet carrier, a second gear ring and a third sun gear;

the four transmission elements are in transmission connection with the first motor, the second motor, the first input shaft and the second input shaft in any corresponding way;

and a first clutch is arranged between any two of the four transmission elements.

Preferably, the compound planetary gear is a C-R compound planetary gear;

the C-R compound planetary gear comprises four transmission elements, and the transmission elements are a fourth sun gear, a third planet carrier/third gear ring, a fourth gear ring/fourth planet carrier and a fifth sun gear;

Preferably, a one-way clutch or a brake for preventing the reverse rotation of the motor is arranged between the power coupling mechanism and the first motor and/or the second motor;

the double-shaft gear box is provided with a reversing gear.

Preferably, the first clutch is an electromagnetically actuated dog clutch.

Preferably, the double-shaft gearbox gear shifting mechanism adopts an electromagnetically-actuated dog clutch or an electromagnetically-actuated shifting fork and synchronizer gear shifting mechanism.

In order to solve the technical problem, the utility model discloses a another technical scheme is:

a vehicle uses the multi-gear dual-motor driving system.

The beneficial effects of the utility model reside in that: when the first clutch is closed, the gear shifting mechanism is engaged into any gear, so that all fixed gears can be realized; when the first clutch is separated, the gear shifting mechanism is used for selecting and engaging an odd gear and an even gear, so that the combination of a plurality of gears can be realized; the first motor, the second motor, the power coupling mechanism and the double-shaft gear box are matched, so that unpowered interrupted gear shifting can be realized; by utilizing the differential characteristic of the planetary gear set and the double-input characteristic of the double-shaft gear box, multiple gear combinations of double motors are formed, the speed ratio change range is widened, and the double motors can operate in a high-efficiency interval under different working conditions and full speed ranges; by adopting the double motors, power redundancy can be provided for the vehicle, and the fault tolerance and reliability of the vehicle are improved.

Drawings

Fig. 1 is a schematic structural diagram of a multi-gear dual-motor driving system of a combination 1 according to a first embodiment of the present invention;

fig. 2 is a schematic structural diagram of a multi-gear dual-motor driving system of a combination 3 according to a first embodiment of the present invention;

fig. 3 is a schematic structural diagram of a multi-gear dual-motor driving system of a combination 4 according to a first embodiment of the present invention;

FIG. 4 is a schematic view of the Lavenner planetary gear;

fig. 5 is a schematic structural diagram of a multi-gear dual-motor driving system of the combination 1 according to the second embodiment of the present invention;

fig. 6 is a schematic structural diagram of a multi-gear dual-motor driving system of the combination 2 according to the second embodiment of the present invention;

FIG. 7 is a schematic view of the C-R compound planetary gear;

fig. 8 is a schematic structural diagram of a multi-gear dual-motor driving system of a combination 1 according to a third embodiment of the present invention;

fig. 9 is a schematic structural diagram of a multi-gear dual-motor driving system of the combination 2 according to the third embodiment of the present invention;

fig. 10 is a schematic structural diagram of a multi-gear dual-motor driving system of a combination 1 in combination with a one-way clutch or a brake according to a first embodiment of the present invention;

fig. 11 is a schematic structural diagram of a multi-gear dual-motor driving system of the combination 1 according to the second embodiment of the present invention, which is combined with a one-way clutch or a brake;

description of reference numerals: 1. a first motor; 2. a second motor; 3. a power coupling mechanism; 31. a first clutch; 32. a first sun gear; 33. a first ring gear; 34. a first carrier; 4. a double-shaft gear box; 41. a first input shaft; 42. a second input shaft; 43. an output shaft; 5. a one-way clutch or brake; 6. a ravigneaux planetary gear; 61. a second sun gear; 62. a second planet carrier; 63. a second ring gear; 64. a third sun gear; 7. a C-R compound planetary gear; 71. a fourth sun gear; 72. a third carrier; 73. a third ring gear; 74. a fourth ring gear; 75. a fourth planet carrier; 76. a fifth sun gear.

Detailed Description

In order to explain the technical content, the objects and the effects of the present invention in detail, the following description is made with reference to the accompanying drawings in combination with the embodiments.

Example one

A multi-gear double-motor driving system comprises a first motor 1, a second motor 2, a power coupling mechanism 3 and a double-shaft gear box 4;

the double-shaft gearbox 4 comprises a gear shifting mechanism, a first input shaft 41, a second input shaft 42 and an output shaft 43, wherein an odd-gear brake gear is arranged on the first input shaft 41, an even-gear driving gear is arranged on the second input shaft 42, each gear driven gear is arranged on the output shaft 43, the gear driving gears are meshed with the corresponding driven gear, one gear in each gear is connected with the shaft where the gear is located through the gear shifting mechanism, namely the gear shifting mechanism controls the transmission connection of the output shaft 43 with the first input shaft 41 and the second input shaft 42;

through adopting gear drive, can get rid of hydraulic system, reduce hydraulic loss, simple structure, it is efficient, with low costs.

The power coupling mechanism 3 comprises a planetary gear set and a first clutch 31, the first motor 1 and the second motor 2 are respectively in transmission connection with the planetary gear set, and the first clutch 31 controls the transmission relationship between the planetary gear set and the first input shaft 41 and the second input shaft 42;

when the first clutch 31 is closed, the gear shifting mechanism of the gear shifting mechanism only engages one gear at a time, and all fixed gears can be realized; when the first clutch 31 is disengaged, the gear shifting mechanism can select and engage one odd gear and one even gear each time, and combination of multiple gears can be realized.

The first motor 1 and the second motor 2 can also be a first motor 1 rotor and a second motor 2 rotor of a double-rotor motor.

The planetary gear set includes three transmission elements, which are a first sun gear 32, a first ring gear 33, a first planet carrier 34;

one of the transmission elements is connected to the first electric machine 1,

the remaining one of the transmission elements is connected to the first input shaft 41,

the remaining one of the transmission elements is connected to the second input shaft 42 and the second electric machine 2;

a first clutch 31 is mounted between any two of the three transmission elements.

The combination form includes:

1. referring to fig. 1, a first ring gear 33 and a first sun gear 32 are respectively connected with a first motor 1 and a second motor 2, a first planet carrier 34 is connected with a first input shaft 41 of a double-shaft gear box 4, and a second input shaft 42 of the double-shaft gear box 4 is connected with the first ring gear 33 or the first sun gear 32;

2. the first gear ring 33 and the first sun gear 32 are respectively connected with the first motor 1 and the second motor 2, the first planet carrier 34 is connected with the second input shaft 42 of the double-shaft gear box 4, and the first input shaft 41 of the double-shaft gear box 4 is connected with the first gear ring 33 or the first sun gear 32;

3. referring to fig. 2, the first ring gear 33 and the first carrier 34 are connected to the first motor 1 and the second motor 2, respectively, and the first ring gear 33 and the first sun gear 32 are connected to the first input shaft 41 and the second input shaft 42 of the two-shaft gear box 4, respectively;

4. referring to fig. 3, the first carrier 34 and the first sun gear 32 are connected to the first motor 1 and the second motor 2, respectively, and the first ring gear 33 and the first sun gear 32 are connected to the first input shaft 41 and the second input shaft 42 of the two-shaft gear box 4, respectively;

5. the first planet carrier 34 and the first gear ring 33 are respectively connected with the first motor 1 and the second motor 2, and the first gear ring 33 and the first sun gear 32 are respectively connected with the first input shaft 41 and the second input shaft 42 of the double-shaft gear box 4;

6. the first planet carrier 34 and the first sun gear 32 are respectively connected with the first motor 1 and the second motor 2, and the first planet carrier 34 and the first sun gear 32 are respectively connected with the first input shaft 41 and the second input shaft 42 of the double-shaft gear box 4;

7. the first planet carrier 34 and the first gear ring 33 are respectively connected with the first motor 1 and the second motor 2, and the first planet carrier 34 and the first gear ring 33 are respectively connected with the first input shaft 41 and the second input shaft 42 of the double-shaft gear box 4;

a one-way clutch or brake 5 for preventing the reverse rotation of the motor is arranged between the power coupling mechanism 3 and the first motor 1 and/or the second motor 2;

the double-shaft gear box 4 is provided with a reverse gear.

A corresponding grade climbing gear of the vehicle is formed by arranging a braking device for preventing the reverse rotation of the motor at the output shaft 43 of the first motor 1, wherein the output torque of the planet row is 1+ k times of the torque of the second motor 2, or T is (1+ k) Tm 2; a braking device for preventing the reverse rotation of the motor can be arranged at the output shaft 43 of the second motor 2, when the output torque of the planet row is 1+1/k times of the torque of the first motor 1, or T ═ 1+1/k) Tm 1; a braking device for preventing the reverse rotation of the motors may be provided at the output shafts 43 of the two motors at the same time. The device may be a brake or a one-way clutch. k is a planet row characteristic parameter, and can be 2 generally. Correspondingly, the double-shaft gearbox 4 should be set to a reverse gear.

The first clutch 31 is an electromagnetically actuated dog clutch.

By adopting the dog clutch, the characteristic that the motor can be started at the rotation speed of 0 directly can be matched, the condition that the lowest rotation speed needs to be kept like a traditional internal combustion engine is not needed, namely, a half-clutch state needs to be kept, and a process and a linear process are needed for power transmission; the dual motors of the present application more match the dog clutch, the contact is rigid, there is no half-clutch state, and the coupling process is non-linear.

The gear shifting mechanism of the double-shaft gear box 4 adopts an electromagnetically actuated dog clutch or an electromagnetically actuated shifting fork and synchronizer gear shifting mechanism.

Example two

A multi-gear dual-motor driving system, the same parts as the first embodiment will not be described again, wherein

The planetary gear set is a compound planetary gear, and the compound planetary gear is a ravigneaux planetary gear 6 (refer to fig. 4);

the ravigneaux planetary gear 6 includes four transmission elements, which are a second sun gear 61 (large), a second carrier 62, a second ring gear 63, and a third sun gear 64 (small);

the four transmission elements are in transmission connection with the first motor 1, the second motor 2, the first input shaft 41 and the second input shaft 42 in any corresponding mode;

a first clutch 31 is mounted between any two of the four transmission elements.

The combination form includes:

1. referring to fig. 5, a rotation shaft of the second ring gear 63 is connected to the power output shaft 43 of the first motor 1, power acts on the planetary gear set through the second ring gear 63, a rotation shaft of the second sun gear 61 is connected to the rotor of the second motor 2, a rotation shaft of the second carrier 62 is connected to the first input shaft 41 of the two-shaft gear box 4, and a rotation shaft of the third sun gear 64 is connected to the second input shaft 42 of the two-shaft gear box 4.

2. Referring to fig. 6, the rotation shafts of the second sun gear 61 and the third sun gear 64 are connected to the rotors of the first motor 1 and the second motor 2, respectively (or the rotation shafts of the second sun gear 61 and the third sun gear 64 are connected to the rotors of the second motor 2 and the first motor 1, respectively), and the rotation shafts of the second ring gear 63 and the second carrier 62 are connected to the first input shaft 41 and the second input shaft 42 of the double-shaft gear box 4, respectively (or the rotation shafts of the second ring gear 63 and the second carrier 62 are connected to the second input shaft 42 and the first input shaft 41 of the double-shaft gear box 4, respectively).

EXAMPLE III

The planetary gear set is a compound planetary gear, and the compound planetary gear is a C-R compound planetary gear 7 (refer to FIG. 7);

the C-R compound planetary gear 7 includes four transmission elements, which are a fourth sun gear 71, a third carrier 72/a third ring gear 73, a fourth ring gear 74/a fourth carrier 75, and a fifth sun gear 76;

a first clutch 31 is mounted between any two of the four transmission elements.

The combination form includes:

1. referring to fig. 8, the fourth sun gear 71 is connected to the second electric machine 2, the fifth sun gear 76 is connected to the even input shaft of the two-shaft gearbox 4, the third carrier 72/third ring gear 73 is connected to the odd input shaft of the two-shaft gearbox 4, and the fourth ring gear 74/fourth carrier 75 is connected to the first electric machine 1. The connecting elements of the first motor 1 and the second motor 2 can be interchanged; the connecting elements of the third carrier 72/third ring gear 73, fourth ring gear 74/fourth carrier 75 are interchangeable.

2. Referring to fig. 9, the fourth sun gear 71 is connected to the second electric machine 2, the fifth sun gear 76 is connected to the first electric machine 1, the third carrier 72/third ring gear 73 is connected to the odd input shaft of the two-shaft gearbox 4, and the fourth ring gear 74/fourth carrier 75 is connected to the even input shaft of the two-shaft gearbox 4. The connecting elements of the first motor 1 and the second motor 2 can be interchanged; the connecting elements of the third carrier 72/third ring gear 73, fourth ring gear 74/fourth carrier 75 are interchangeable.

The method for realizing the gear shifting control without power interruption comprises the following steps:

the first embodiment (see fig. 10) or the second embodiment (see fig. 11) in combination, both of which have the same principle;

judging whether the system is currently in an odd gear i or an even gear j;

shifting from odd gears to even gears:

torque control of the first motor 1 and the second motor 2, distributing the torque of the first motor 1 and the torque of the second motor 2, unloading the torque on the first clutch 31, and separating the first clutch 31;

the first motor 1 controls the torque to drive the vehicle, the second motor 2 controls the rotating speed, and the speed is regulated to enable an input shaft connected with the double-shaft gear box 4 to be synchronous with an i +1 gear or a (i-1 gear) gear;

controlling a gear shifting mechanism to be in a gear (i + 1) or a gear (i-1), controlling the torque of a first motor 1, and driving a vehicle;

the torque of the second motor 2 is reduced, the torque of the first motor 1 is increased to compensate, the torque of the gear shifting mechanism at the gear i is unloaded, and the gear i is removed;

controlling the rotating speed of the first motor 1 to enable the target rotating speed to be consistent with that of the second motor 2, and combining the first clutch 31;

and controlling the torque of the first motor 1 and the second motor 2, recovering the driving and finishing the gear shifting.

Odd gears are shifted by even gears:

controlling the torque of the first motor 1 and the second motor 2, unloading the first motor 1, increasing the torque of the second motor 2, unloading the torque on the first clutch 31, and separating the first clutch 31;

the torque of the second motor 2 is controlled to drive the vehicle, the rotating speed of the first motor 1 is controlled, and the speed is regulated to enable an input shaft connected with the double-shaft gear box 4 to be synchronous with a gear of j +1 gear or (gear of j-1);

adjusting the torques of the first motor 1 and the second motor 2 to meet the torque relation of the balance state of the planetary gear set, unloading the torque of the gear shifting mechanism at the gear j, and removing the gear j;

controlling the rotating speed of the second motor 2 to make the target rotating speed consistent with that of the first motor 1, and combining the first clutch 31;

The gear combinations that can be realized are:

mode(s)

First motor

Second electric machine

Brake

First clutch

1 gear is hung

2-gear engaging

3-gear shift

4-gear shift

1

-

Climbing block

Bonding of

Releasing

√

2

1 gear

Releasing

Bonding of

√

3

2 keeps off

Releasing

Bonding of

√

4

3 grade

Releasing

Bonding of

√

5

4-gear

Releasing

Bonding of

√

6

Differential speed

Releasing

√

7

12 gear

Releasing

√

8

Differential speed

Releasing

√

9

23 gear

Releasing

√

10

Differential speed

Releasing

√

11

34 stop

Releasing

√

12

Differential speed

Releasing

√

Example four

A vehicle uses the multi-gear dual-motor driving system of any one of the first embodiment to the third embodiment.

To sum up, the utility model provides a pair of two motor drive systems of many grades is applicable to passenger car and commercial car, and the specially adapted is unloaded and the great commercial car of full load operating mode quality difference. By utilizing the differential characteristic of the planetary gear train and the double-input characteristic of the double-shaft gear box, multiple gear combinations of double motors are formed, the speed ratio change range is widened, and the double motors can operate in a high-efficiency interval under different working conditions and full speed ranges. The dual motors are used for driving, and special climbing gears can be arranged, so that the dynamic performances of acceleration, climbing and the like of the vehicle are improved. Through the drive power that provides jointly of two electricity, can realize unpowered interruption and shift, promote the quality of shifting. The gear transmission is adopted, a hydraulic system can be removed, hydraulic loss is reduced, the structure is simple, the efficiency is high, and the cost is low. The double motors are adopted, so that power redundancy can be provided for the vehicle, and the fault tolerance and reliability of the vehicle are improved.

The above mentioned is only the embodiment of the present invention, and not the limitation of the patent scope of the present invention, all the equivalent transformations made by the contents of the specification and the drawings, or the direct or indirect application in the related technical field, are included in the patent protection scope of the present invention.

Claims

1. A multi-gear dual-motor driving system is characterized by comprising a first motor, a second motor, a power coupling mechanism and a dual-shaft gear box;

2. The multiple speed, dual motor drive system as claimed in claim 1, wherein said planetary gear set includes three transmission elements, said transmission elements being a first sun gear, a first ring gear, a first planet carrier;

one of the transmission elements is connected with the first motor,

3. The multiple speed, dual motor drive system as claimed in claim 1, wherein said planetary gear set is a compound planetary gear.

4. The multiple speed, dual motor drive system as claimed in claim 3, wherein the compound planetary gear is a ravigneaux planetary gear;

5. The multi-speed, dual motor drive system as defined in claim 3, wherein the compound planetary gear is a C-R compound planetary gear;

6. The multi-gear dual motor drive system according to any one of claims 1-5, wherein a one-way clutch or brake for preventing the reverse rotation of the motor is arranged between the power coupling mechanism and the first motor and/or the second motor;

the double-shaft gear box is provided with a reversing gear.

7. The multiple speed, dual motor drive system as claimed in any one of claims 1-5, wherein the first clutch is an electromagnetically actuated dog clutch.

8. The multiple speed dual motor drive system as claimed in any one of claims 1 to 5, wherein the dual shaft gearbox shifting mechanism employs an electromagnetically actuated dog clutch or an electromagnetically actuated fork plus synchronizer shifting mechanism.

9. A vehicle, characterized in that a multi-gear dual motor drive system according to any one of claims 1-8 is used.