CN115419685A

CN115419685A - Double-motor hybrid gearbox and operation machine

Info

Publication number: CN115419685A
Application number: CN202211073932.XA
Authority: CN
Inventors: 陈小江; 李文祥; 孙全斌; 李永坚; 刘金强; 王明
Original assignee: Hunan Xingbida Netlink Technology Co Ltd
Current assignee: Hunan Xingbida Netlink Technology Co Ltd
Priority date: 2022-07-28
Filing date: 2022-09-02
Publication date: 2022-12-02
Also published as: WO2024045549A1

Abstract

The invention provides a double-motor hybrid gearbox and an operation machine, wherein the system comprises: the first input shaft is selectively linked with the first gear shifting mechanism and the second gear shifting mechanism respectively, and is selectively linked with the third gear shifting mechanism and the fourth gear shifting mechanism respectively through the first intermediate shaft and the second intermediate shaft; the second input shaft and the third input shaft are selectively linked with the first gear shifting mechanism respectively, and are selectively linked with the second gear shifting mechanism, the third gear shifting mechanism and the fourth gear shifting mechanism respectively through the first intermediate shaft and the second intermediate shaft; the output shaft is selectively linked with the first input shaft and/or the second input shaft and/or the third input shaft through the first gear shifting mechanism, the second gear shifting mechanism, the third gear shifting mechanism and the fourth gear shifting mechanism respectively so as to realize switching among a plurality of gears. The invention realizes two sets of motor system power transmission paths by arranging the dual-motor offset framework, can independently output and simultaneously share the mechanical transmission path with the same gear.

Description

Double-motor hybrid gearbox and operation machine

Technical Field

The invention relates to the technical field of transmission, in particular to a double-motor hybrid gearbox and an operation machine.

Background

With the development of the hybrid electric and gasoline technology, the field of application of the hybrid electric and gasoline technology is gradually increased, although the hybrid electric and gasoline technology applied to the saloon car is mature, the load of the saloon car is light, the gear applied to the transmission system of the saloon car cannot be adapted to a heavy-duty vehicle, particularly, the hybrid power transmission system applied to the commercial vehicle mainly adopts a single-motor P2 parallel hybrid architecture, the fuel saving effect of the P2 hybrid system under the urban working condition is obviously lower than that of a double-motor power splitting and series-parallel hybrid system, the power interruption problem exists in the P2 hybrid power during gear shifting, the driving performance of the vehicle and the safety of climbing gear shifting are seriously affected when the power interruption occurs in the heavy-duty vehicle, therefore, under the large background of the hybrid electric and gasoline technology, the development of the hybrid electric and gasoline technology is suitable for the heavy-duty vehicle, and how to solve the power interruption and the better fuel saving rate in the gear shifting process becomes a technical problem in the field.

Disclosure of Invention

The invention provides a double-motor hybrid gearbox, which is used for solving the defects in the prior art.

The invention also provides a working machine.

According to a first aspect of the present invention, there is provided a dual-motor hybrid transmission, comprising: the gear shifting mechanism comprises an engine, a first motor, a second motor, a first input shaft, a second input shaft, a third input shaft, a first intermediate shaft, a second intermediate shaft, a gear assembly, a first gear shifting mechanism, a second gear shifting mechanism, a third gear shifting mechanism, a fourth gear shifting mechanism and an output shaft;

the first input shaft is connected with the engine, the second input shaft is connected with the first motor, and the third input shaft is connected with the second motor;

the second input shaft, the third input shaft, the first intermediate shaft and the second intermediate shaft are respectively arranged in parallel with the first input shaft;

the gear assemblies are arranged on the first input shaft, the second input shaft, the third input shaft, the first intermediate shaft, the second intermediate shaft and the output shaft;

the first input shaft is selectively linked with the first gear shifting mechanism and the second gear shifting mechanism respectively, and is selectively linked with the third gear shifting mechanism and the fourth gear shifting mechanism respectively through the first intermediate shaft and the second intermediate shaft;

the second input shaft and the third input shaft are selectively linked with the first gear shifting mechanism respectively, and are selectively linked with the second gear shifting mechanism, the third gear shifting mechanism and the fourth gear shifting mechanism respectively through the first intermediate shaft and the second intermediate shaft;

the output shaft is selectively linked with the first input shaft and/or the second input shaft and/or the third input shaft through the first gear shifting mechanism, the second gear shifting mechanism, the third gear shifting mechanism and the fourth gear shifting mechanism respectively so as to realize switching among a plurality of gears;

wherein the first and second shift mechanisms are disposed on the first input shaft;

the third gear shifting mechanism and the fourth gear shifting mechanism are arranged on the output shaft.

Optionally, the method further comprises: the clutch is respectively connected with the power shaft of the engine and the first input shaft so as to realize selectable linkage between the engine and the first input shaft.

Optionally, at least two first intermediate shafts are uniformly distributed around the circumference of the first input shaft; and/or at least two second intermediate shafts are uniformly distributed around the circumference of the first input shaft.

Optionally, the gear assembly comprises: a first gear pair and a second gear pair; the first gear pair is respectively connected with the first input shaft and the second input shaft so as to realize linkage of the first input shaft and the second input shaft; the second gear pair is connected with the first input shaft and the third input shaft respectively and is arranged corresponding to the first gear shifting mechanism so as to realize switching among a plurality of gears.

Optionally, the gear assembly further comprises: a third gear pair, a fourth gear pair, a fifth gear pair and a sixth gear pair; the third gear pair is respectively connected with the first input shaft and the first middle shaft and is arranged corresponding to the first gear shifting mechanism so as to realize the switching among a plurality of gears; the fourth gear pair is respectively connected with the first input shaft and the first middle shaft and is arranged corresponding to the first gear shifting mechanism so as to realize the switching among a plurality of gears; the fifth gear pair is connected with the output shaft and the first intermediate shaft respectively and is arranged corresponding to the fourth gear shifting mechanism so as to realize the switching among a plurality of gears; and the sixth gear pair is connected with the output shaft and the first intermediate shaft respectively and is arranged corresponding to the fourth gear shifting mechanism so as to realize the switching among a plurality of gears.

Optionally, the gear assembly further comprises: a seventh gear pair, an eighth gear pair, a ninth gear pair and a tenth gear pair; the seventh gear pair is connected with the first input shaft and the second intermediate shaft respectively and is arranged between the first gear shifting mechanism and the second gear shifting mechanism so as to realize the switching among a plurality of gears; the eighth gear pair is connected with the output shaft and the second intermediate shaft respectively and is arranged corresponding to the second gear shifting mechanism so as to realize switching among a plurality of gears; the ninth gear pair is connected with the output shaft and the second intermediate shaft respectively and is arranged corresponding to the third gear shifting mechanism so as to realize the switching among a plurality of gears; the tenth gear pair is connected with the output shaft and the second intermediate shaft respectively and is arranged corresponding to the third gear shifting mechanism so as to realize switching among a plurality of gears.

Optionally, the output shaft and the second intermediate shaft perform a plurality of gear shifts through the tenth gear pair and the third gear shift mechanism, including at least a reverse gear.

Optionally, the gear assembly further comprises: an eleventh gear pair, a twelfth gear pair, a thirteenth gear pair, a fourteenth gear pair and a fifteenth gear pair; the eleventh gear pair is connected with the first input shaft and the first intermediate shaft respectively and is arranged corresponding to the first gear shifting mechanism so as to realize switching among a plurality of gears; the twelfth gear pair is connected with the first input shaft and the first intermediate shaft respectively and is arranged corresponding to the first gear shifting mechanism so as to realize the switching among a plurality of gears; the thirteenth gear pair is arranged outside the output shaft and the first intermediate shaft and corresponds to the third gear shifting mechanism so as to realize switching among a plurality of gears; the fourteenth gear pair is connected with the output shaft and the first intermediate shaft respectively and is arranged corresponding to the fourth gear shifting mechanism so as to realize switching among a plurality of gears; the fifteenth gear pair is connected with the output shaft and the first intermediate shaft respectively and is arranged corresponding to the fourth gear shifting mechanism so as to realize switching among a plurality of gears.

Optionally, the gear assembly further comprises: a sixteenth gear pair, a seventeenth gear pair and an eighteenth gear pair; the sixteenth gear pair is connected with the first input shaft and the second middle shaft respectively and is arranged between the first gear shifting mechanism and the second gear shifting mechanism so as to realize switching among a plurality of gears; the seventeenth gear pair is connected with the output shaft and the second middle shaft respectively and is arranged corresponding to the second gear shifting mechanism so as to realize switching among a plurality of gears; and the eighteenth gear pair is connected with the output shaft and the second intermediate shaft respectively and corresponds to the third gear shifting mechanism so as to realize the switching among a plurality of gears.

Optionally, the gear assembly further comprises: an eleventh gear pair, a twelfth gear pair, a thirteenth gear pair, a fourteenth gear pair and a fifteenth gear pair; the eleventh gear pair is connected with the first input shaft and the first intermediate shaft respectively and is arranged corresponding to the first gear shifting mechanism so as to realize switching among a plurality of gears; the twelfth gear pair is connected with the first input shaft and the first middle shaft respectively and is arranged corresponding to the first gear shifting mechanism so as to realize switching among a plurality of gears; the thirteenth gear pair is respectively connected with the output shaft and the outer part of the first intermediate shaft and is arranged corresponding to the second gear shifting mechanism so as to realize the switching among a plurality of gears, the fourteenth gear pair is respectively connected with the output shaft and the first intermediate shaft and is arranged corresponding to the third gear shifting mechanism so as to realize the switching among a plurality of gears; the fifteenth gear pair is connected with the output shaft and the first intermediate shaft respectively and is arranged corresponding to the third gear shifting mechanism so as to realize switching among a plurality of gears.

Optionally, the gear assembly further comprises: a sixteenth gear pair, a seventeenth gear pair and an eighteenth gear pair; the sixteenth gear pair is connected with the first input shaft and the second intermediate shaft respectively and is arranged between the first gear shifting mechanism and the second gear shifting mechanism so as to realize the switching among a plurality of gears; the seventeenth gear pair is connected with the output shaft and the second middle shaft respectively and is arranged corresponding to the fourth gear shifting mechanism so as to realize the switching among a plurality of gears; and the eighteenth gear pair is connected with the output shaft and the second intermediate shaft respectively and corresponds to the fourth gear shifting mechanism so as to realize the switching among a plurality of gears.

According to a second aspect of the present invention, there is provided a working machine having the above-described two-motor hybrid transmission.

One or more technical solutions in the present invention have at least one of the following technical effects: according to the double-motor hybrid transmission case and the operation machine, the double-motor offset framework is arranged, so that two sets of motor system power transmission paths can be independently output under various working conditions, mechanical transmission paths with the same gear can be shared, respective gear shifting without power interruption can be realized, the double-motor systems are arranged in an offset mode along the circumferential direction of the central shaft, the reduction ratio of the input end is increased, the torque of the double-motor systems is greatly reduced, the rotating speed of the motors is increased, the traction motor with small size, light weight and low cost can be adopted to meet the wheel driving requirement, and the transmission system is more compact in structure, reasonable in layout and high in cost performance.

Drawings

In order to more clearly illustrate the present invention or the technical solutions in the prior art, the drawings used in the embodiments or the description of the prior art will be briefly introduced below, and it is obvious that the drawings in the following description are some embodiments of the present invention, and other drawings can be obtained by those skilled in the art without creative efforts.

FIG. 1 is one of the schematic layout diagrams of a dual motor hybrid transmission provided by the present invention;

FIG. 2 is a second schematic layout diagram of the dual-motor hybrid transmission provided by the present invention;

FIG. 3 is a third schematic layout diagram of the dual-motor hybrid transmission provided by the present invention;

FIG. 4 is a fourth schematic layout diagram of the dual-motor hybrid transmission provided by the present invention;

FIG. 5 is a fifth schematic layout diagram of the dual-motor hybrid transmission provided by the present invention;

fig. 6 is a sixth schematic layout view of the two-motor hybrid transmission according to the present invention.

Reference numerals:

1. an engine; 2. a first motor; 3. a second motor; 4. a clutch;

10. a first input shaft; 20. a second input shaft; 30. a third input shaft; 40. a first intermediate shaft; 50. a second intermediate shaft; 60. an output shaft;

70. a first gear pair; 71. a second gear pair; 72. a third gear pair; 73. a fourth gear pair; 74. a fifth gear pair; 75. a sixth gear pair; 76. a seventh gear pair; 77. an eighth gear pair; 78. a ninth gear pair; 79. a tenth gear pair; 80. an eleventh gear pair; 81. a twelfth gear pair; 82. a thirteenth gear pair; 83. a fourteenth gear pair; 84. a fifteenth gear pair; 85. a sixteenth gear pair; 86. a seventeenth gear pair; 87. an eighteenth gear pair;

k1, a first gear shifting mechanism; k2, a second gear shifting mechanism; k3, a third gear shifting mechanism; k4 and a fourth gear shifting mechanism.

Detailed Description

In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are some, but not all, embodiments of the present invention. All other embodiments, which can be obtained by a person skilled in the art without any inventive step based on the embodiments of the present invention, are within the scope of the present invention.

In some embodiments of the present invention, as shown in fig. 1 to 4, the present solution provides a dual-motor hybrid transmission, comprising: the transmission comprises an engine 1, a first motor 2, a second motor 3, a first input shaft 10, a second input shaft 20, a third input shaft 30, a first intermediate shaft 40, a second intermediate shaft 50, a gear assembly, a first gear shifting mechanism K1, a second gear shifting mechanism K2, a third gear shifting mechanism K3, a fourth gear shifting mechanism K4 and an output shaft 60;

the first input shaft 10 is connected with the engine 1, the second input shaft 20 is connected with the first motor 2, and the third input shaft 30 is connected with the second motor 3;

the second input shaft 20, the third input shaft 30, the first intermediate shaft 40 and the second intermediate shaft 50 are respectively arranged in parallel with the first input shaft 10;

gear assemblies are arranged on the first input shaft 10, the second input shaft 20, the third input shaft 30, the first intermediate shaft 40, the second intermediate shaft 50 and the output shaft 60;

the first input shaft 10 is selectively linked with the first gear shifting mechanism K1 and the second gear shifting mechanism K2 respectively, and selectively linked with the third gear shifting mechanism K3 and the fourth gear shifting mechanism K4 through the first intermediate shaft 40 and the second intermediate shaft 50 respectively;

the second input shaft 20 and the third input shaft 30 are selectively linked with the first gear shifting mechanism K1 respectively, and selectively linked with the second gear shifting mechanism K2, the third gear shifting mechanism K3 and the fourth gear shifting mechanism K4 respectively through the first intermediate shaft 40 and the second intermediate shaft 50;

the output shaft 60 is selectively linked with the first input shaft 10 and/or the second input shaft 20 and/or the third input shaft 30 through the first gear shifting mechanism K1, the second gear shifting mechanism K2, the third gear shifting mechanism K3 and the fourth gear shifting mechanism K4 respectively to realize switching among a plurality of gears;

the first gear shifting mechanism K1 and the second gear shifting mechanism K2 are arranged on the first input shaft 10;

the third shift mechanism K3 and the fourth shift mechanism K4 are provided on the output shaft 60.

It should be noted that, in the power transmission system of the present invention, by providing the first intermediate shaft 40 and the second intermediate shaft 50, a plurality of different working conditions of the series-parallel hybrid of the three power sources can be realized, a plurality of power transmission paths are constructed in the power transmission system, and in the process of shifting gears in the power transmission system, the power of the power transmission system is not interrupted by switching among the plurality of power transmission paths, so that the smoothness of the power transmission system is improved by using the transmission system with a simple structure, the cost of the power transmission system is reduced, and the jerk in the driving process is reduced.

In some possible embodiments of the present invention, the method further includes: the clutch 4 is connected with a power shaft of the engine 1 and the first input shaft 10 respectively, so that the engine 1 and the first input shaft 10 can be selectively linked.

Specifically, the embodiment provides an implementation mode of the clutch 4, and by arranging the clutch 4, switching among various mixed-action working conditions of the engine 1, the first motor 2 and the second motor 3 is realized, and selective engagement linkage or disconnection independent driving of two sets of intermediate shaft mechanical shaft-gear mechanisms is realized, so that gear sharing driven by three power sources is established, and efficient driving in a full vehicle speed range is realized.

It should be noted that, because the engine 1, the first motor 2 and the second motor 3 have independent driving paths, one power path is kept to be driven at the current gear during the gear shifting, and the other power path is unloaded for gear shifting, so that the gear shifting control without power interruption is realized, and the driving smoothness is improved.

In some possible embodiments of the invention, at least two first intermediate shafts 40 are arranged uniformly around the circumference of the first input shaft 10;

and/or at least two second intermediate shafts 50 are uniformly distributed around the circumference of the first input shaft 10.

Specifically, the embodiment provides an implementation manner of first jackshaft 40 and second jackshaft 50, through set up a plurality of first jackshafts 40 and/or a plurality of second jackshafts 50 around first input shaft 10 circumference equipartition, has promoted the bearing capacity of drive load, has satisfied the demand of great load application scenario for shift unpowered interruption, high reliability, high security, high performance-price ratio.

In a possible embodiment, as shown in fig. 1 and 3, a dual countershaft architecture with two first countershafts 40 and two second countershafts 50 is used, which enables a higher drive load application scenario.

It should be noted that, in the power transmission system provided by the present invention, by providing the first intermediate shaft 40 and the second intermediate shaft 50, a plurality of different working conditions of the series-parallel hybrid of the three power sources can be realized, a plurality of power transmission paths are constructed in the power transmission system, and in the process of shifting the power transmission system, the power of the power transmission system is not interrupted by switching among the plurality of power transmission paths, so that the smoothness of the power transmission system is improved by applying the transmission system with a simple structure, the cost of the power transmission system is reduced, and the jerking feeling in the driving process is reduced.

In some possible embodiments of the invention, the gear assembly comprises: a first gear pair 70 and a second gear pair 71; the first gear pair 70 is respectively connected with the first input shaft 10 and the second input shaft 20 to realize the linkage of the first input shaft 10 and the second input shaft 20; the second gear pair 71 is connected to the first input shaft 10 and the third input shaft 30, respectively, and is disposed corresponding to the first shift mechanism K1 to realize switching between a plurality of gears.

Specifically, the present embodiment provides an embodiment of the first gear pair 70 and the second gear pair 71, and the first gear pair 70 and the second gear pair 71 are arranged to enable a synchronous action between the first input shaft 10 and the second input shaft 20.

In some possible embodiments of the invention, the gear assembly further comprises: third gear set 72, fourth gear set 73, fifth gear set 74, and sixth gear set 75; the third gear pair 72 is connected with the first input shaft 10 and the first intermediate shaft 40 respectively and is arranged corresponding to the first gear shift mechanism K1 to realize switching among a plurality of gears; the fourth gear pair 73 is connected with the first input shaft 10 and the first intermediate shaft 40 respectively and is arranged corresponding to the first gear shift mechanism K1 to realize switching among a plurality of gears; the fifth gear pair 74 is connected to the output shaft 60 and the first intermediate shaft 40, and is disposed corresponding to the fourth gear shift mechanism K4, so as to realize switching among a plurality of gears; the sixth gear pair 75 is connected to the output shaft 60 and the first countershaft 40, respectively, and is provided corresponding to the fourth shift mechanism K4 to realize switching between a plurality of gears.

Specifically, the present embodiment provides an embodiment of third gear pair 72, fourth gear pair 73, fifth gear pair 74 and sixth gear pair 75, and by providing third gear pair 72, fourth gear pair 73, fifth gear pair 74 and sixth gear pair 75, switching of output shaft 60 between multiple gears is achieved.

In some possible embodiments of the invention, the gear assembly further comprises: seventh gear set 76, eighth gear set 77, ninth gear set 78 and tenth gear set 79; the seventh gear pair 76 is connected with the first input shaft 10 and the second intermediate shaft 50 respectively and is arranged between the first gear shifting mechanism K1 and the second gear shifting mechanism K2 to realize the switching among a plurality of gears; the eighth gear pair 77 is connected to the output shaft 60 and the second intermediate shaft 50, respectively, and is disposed corresponding to the second shift mechanism K2 to realize switching among a plurality of gears; the ninth gear pair 78 is connected to the output shaft 60 and the second intermediate shaft 50, respectively, and is disposed corresponding to the third shift mechanism K3 to realize switching among a plurality of gears; the tenth gear pair 79 is connected to the output shaft 60 and the second intermediate shaft 50, respectively, and is provided corresponding to the third shift mechanism K3 to realize switching between a plurality of gears.

Specifically, the present embodiment provides an embodiment of the seventh gear pair 76, the eighth gear pair 77, the ninth gear pair 78 and the tenth gear pair 79, and the switching of the output shaft 60 between the plurality of gears is realized by providing the seventh gear pair 76, the eighth gear pair 77, the ninth gear pair 78 and the tenth gear pair 79.

In some possible embodiments of the invention, the output shaft 60 and the second countershaft 50 are shifted through a plurality of gears, including at least reverse, by the tenth gear set 79 and the third gear shift mechanism K3.

Specifically, the present embodiment provides an embodiment in which the output shaft 60 and the second intermediate shaft 50 realize reverse gear through the tenth gear pair 79 and the third shift mechanism K3, and the reverse gear is switched by providing a reverse idle gear in the tenth gear pair 79.

It should be noted that, for the sake of economy, the present invention does not describe the specific structure of the tenth gear pair 79, and in practical applications, the tenth gear pair 79 can refer to fig. 1 and 2, and related arrangements in the art, as shown in fig. 1, the tenth gear pair 79 includes three gears, which are respectively disposed on the second intermediate shaft 50 and the output shaft 60, and are engaged through the reverse idle gear, so as to realize the reverse gear.

In an application scenario, as shown in fig. 1 and fig. 2, the engine 17 is in a gear and reverse gear transmission path, wherein in the seventh gear, the engine 1 can be directly driven with high efficiency, and the transmission path is the simplest; when the engine 1 and the first motor 2 are driven in parallel at the first gear G1, the fourth gear G4 and the seventh gear G7, the second motor 3 can be out of gear and stopped, so that the efficient direct-drive function of the engine 1 under the cruising working condition is realized, and the efficient direct-drive function is as follows:

the transmission path of the first gear G1 of the engine 1 is: the engine 1 → the clutch 4 → the first input shaft 10 → the seventh gear pair 76 → the second intermediate shaft 50 → the ninth gear pair 78 → the third shift mechanism K3 → the output shaft 60.

The transmission path of the second gear G2 of the engine 1 is: the engine 1 → the clutch 4 → the first input shaft 10 → the first shift mechanism K1 → the third gear pair 72 → the first intermediate shaft 40 → the sixth gear pair 75 → the fourth shift mechanism K4 → the output shaft 60.

The transmission path of the third gear G3 of the engine 1 is: the engine 1 → the clutch 4 → the first input shaft 10 → the first shift mechanism K1 → the fourth gear pair 73 → the first intermediate shaft 40 → the sixth gear pair 75 → the fourth shift mechanism K4 → the output shaft 60.

The transmission path of the fourth gear G4 of the engine 1 is: engine 1 → clutch 4 → first input shaft 10 → seventh gear pair 76 → second intermediate shaft 50 → eighth gear pair 77 → second shift mechanism K2 → output shaft 60.

The transmission path of the fifth gear G5 of the engine 1 is: the engine 1 → the clutch 4 → the first input shaft 10 → the first shift mechanism K1 → the third gear pair 72 → the first intermediate shaft 40 → the fifth gear pair 74 → the fourth shift mechanism K4 → the output shaft 60.

The transmission path of the sixth gear G6 of the engine 1 is: the engine 1 → the clutch 4 → the first input shaft 10 → the first shift mechanism K1 → the fourth gear pair 73 → the first intermediate shaft 40 → the fifth gear pair 74 → the fourth shift mechanism K4 → the output shaft 60.

The transmission path of the seventh gear G7 of the engine 1 is: the engine 1 → the clutch 4 → the first input shaft 10 → the second shift mechanism K2 → the output shaft 60.

Transmission path of reverse gear GR of engine 1: the engine 1 → the clutch 4 → the first input shaft 10 → the seventh gear pair 76 → the second intermediate shaft 50 → the tenth gear pair 79 → the third shift mechanism K3 → the output shaft 60.

In one application scenario, as shown in fig. 1 and fig. 2, the first electric machine 2 shares 7 gears and a reverse gear transmission path, wherein the clutch 4 is closed, and the first electric machine 2 shares 7 forward gears and 1 reverse gear of the engine 1 to be linked in parallel; clutch 4 opens, and first motor 2 can keep off the position according to 7 and pure electric drive jointly in 6 fender positions with second motor 3, both can pure electric forward drive, can reverse gear pure electric drive again, specifically as follows:

the transmission path of the first gear G1 of the first electric machine 2 is: the first motor 2 → the first gear pair 70 → the seventh gear pair 76 → the second intermediate shaft 50 → the ninth gear pair 78 → the third shift mechanism K3 → the output shaft 60.

The transmission path of the second gear G2 of the first electric machine 2 is: the first electric motor 2 → the second input shaft 20 → the first gear pair 70 → the first input shaft 10 → the first shift mechanism K1 → the third gear pair 72 → the first intermediate shaft 40 → the sixth gear pair 75 → the fourth shift mechanism K4 → the output shaft 60.

The transmission path of the third gear G3 of the first electric machine 2 is: the first electric motor 2 → the second input shaft 20 → the first gear pair 70 → the first input shaft 10 → the first shift mechanism K1 → the fourth gear pair 73 → the first intermediate shaft 40 → the sixth gear pair 75 → the fourth shift mechanism K4 → the output shaft 60.

The transmission path of the fourth gear G4 of the first electric machine 2 is: the first electric motor 2 → the second input shaft 20 → the first gear pair 70 → the first input shaft 10 → the seventh gear pair 76 → the second intermediate shaft 50 → the eighth gear pair 77 → the second shift mechanism K2 → the output shaft 60.

The transmission path of the fifth gear G5 of the first electric machine 2 is: the first electric motor 2 → the second input shaft 20 → the first gear pair 70 → the first input shaft 10 → the first shift mechanism K1 → the third gear pair 72 → the first intermediate shaft 40 → the fifth gear pair 74 → the fourth shift mechanism K4 → the output shaft 60.

The transmission path of the sixth gear G6 of the first electric machine 2 is: the first electric motor 2 → the second input shaft 20 → the first gear pair 70 → the first input shaft 10 → the first shift mechanism K1 → the fourth gear pair 73 → the first intermediate shaft 40 → the fifth gear pair 74 → the fourth shift mechanism K4 → the output shaft 60.

The transmission path of the seventh gear G7 of the first electric machine 2 is: the first motor 2 → the second input shaft 20 → the first gear pair 70 → the first input shaft 10 → the second shift mechanism K2 → the output shaft 60.

The transmission path of the reverse gear of the engine 1 (the gear is not used for the pure electric drive of the first electric machine 2) is: the first motor 2 → the second input shaft 20 → the first gear pair 70 → the first input shaft 10 → the seventh gear pair 76 → the second intermediate shaft 50 → the tenth gear pair 79 → the third shift mechanism K3 → the output shaft 60.

In one application scenario, as shown in fig. 1 and 2, the second electric machine 3 provides 6 gear transmission paths, wherein the second electric machine 3 can be driven together with the engine 1 and/or the first electric machine 2 in the first gear G1, the second gear G2, the fourth gear G4, the fifth gear G5, the seventh gear G7 and the reverse gear GR of the engine 1, and the engine 1 and the first electric machine 2 can be driven independently of the second electric machine 3 in the third gear G3, the sixth gear G6 and the ninth gear G9, so as to provide a non-power-interruption gear shift for the gear shift of the second electric machine 3, as follows:

the transmission path of the first gear G1 of the second electric machine 3 is: the second electric motor 3 → the third input shaft 30 → the second gear pair 71 → the first shift mechanism K1 → the seventh gear pair 76 → the second intermediate shaft 50 → the tenth gear pair 79 → the third shift mechanism K3 → the output shaft 60.

The transmission path of the second gear G2 of the second electric machine 3 is: the second electric motor 3 → the third input shaft 30 → the second gear pair 71 → the third gear pair 72 → the first intermediate shaft 40 → the sixth gear pair 75 → the fourth shift mechanism K4 → the output shaft 60.

The transmission path of the fourth gear G4 of the second electric machine 3 is: the second electric motor 3 → the third input shaft 30 → the second gear pair 71 → the first shift mechanism K1 → the seventh gear pair 76 → the second intermediate shaft 50 → the eighth gear pair 77 → the second shift mechanism K2 → the output shaft 60.

The transmission path of the fifth gear G5 of the second electric machine 3 is: the second electric motor 3 → the third input shaft 30 → the second gear pair 71 → the third gear pair 72 → the first intermediate shaft 40 → the fifth gear pair 74 → the fourth shift mechanism K4 → the output shaft 60.

The transmission path of the seventh gear G7 of the second electric machine 3 is: the second electric motor 3 → the third input shaft 30 → the second gear pair 71 → the first shift mechanism K1 → the first input shaft 10 → the second shift mechanism K2 → the output shaft 60.

The transmission path of the reverse gear of the engine 1 (the gear is not used for the pure electric drive of the first electric machine 2) is: the second electric motor 3 → the third input shaft 30 → the second gear pair 71 → the first shift mechanism K1 → the seventh gear pair 76 → the second intermediate shaft 50 → the tenth gear pair 79 → the third shift mechanism K3 → the output shaft 60.

In a possible embodiment, the pure electric drive function, the clutch 4 is opened, the engine 1 is stopped, the first electric machine 2 can be driven in 9 gears and the second electric machine 3 can be driven in 6 gears of the first gear G1, the third gear G3, the fourth gear G4, the sixth gear G6, the seventh gear G7 and the ninth gear G9; since there is no reverse gear setting of the engine 1, the reverse gear function is realized by the second electric machine 3 or dual electric machine drive. The first electric machine 2 can be driven in a third gear G3, a sixth gear G6 and a ninth gear G9 independently and electrically, and the second electric machine 3 can be driven in a first gear G1, a fourth gear G4 or a seventh gear G7.

In a possible embodiment, the parallel hybrid function, the clutch 4 closed, the engine 1 and the first electric machine 2 driven in parallel in the 9 gears mentioned above, the second electric machine 3 can be driven jointly in parallel in 6 gears of the first gear G1, the third gear G3, the fourth gear G4, the sixth gear G6, the seventh gear G7 and the ninth gear G9; when the engine 1 and the first motor 2 are driven in parallel at the third gear G3, the sixth gear G6 and the ninth gear G9, the second motor 3 can be disengaged and stopped, so as to improve the transmission efficiency, or power compensation is provided for the engine 1 and the first motor 2 when the first gear G1, the fourth gear G4 or the seventh gear G7 are used for gear shifting independently.

In a possible implementation mode, the series hybrid mode is adopted, the vehicle is frequently started and stopped under the low-load urban working condition, and the oil saving rate is high when the electric quantity of the vehicle-mounted power battery is insufficient. In the series hybrid mode, the clutch 4 is closed, the engine 1 and the first motor 2 are in out-of-gear linkage, the first motor 2 works in the rotating speed mode to provide negative torque, mechanical input power of the engine 1 is converted into electric energy, and the electric energy is connected in series to generate electricity to charge a power battery, or part of the electric energy is directly provided for a controller of the second motor 3 to directly drive wheels. The second electric machine 3 can be driven exclusively in the first gear G1, fourth gear G4 or seventh gear G7.

In a possible embodiment, the engine 1 is controlled to shift smoothly, during driving, the engine 1 needs to shift, firstly, the engine 1 and the first electric machine 2 keep driving, and the second electric machine 3 keeps or shifts into an independent driving gear: 1, 4 or 7, unloading the engine 1 and the first motor 2 at the same time, loading the second motor 3 for driving, opening the clutch 4 after the engine 1 is unloaded, unloading the first motor 2 at the same time, and controlling the corresponding gear shifting mechanism to enter a neutral gear; and then controlling the clutch 4 to be smoothly closed, enabling the first motor 2 to enter a rotating speed mode, enabling the first motor 2 to drive the engine 1 to be controlled to be close to the synchronous rotating speed of the next gear, opening the clutch 4, unloading the first motor 2, controlling a corresponding gear shifting mechanism to enable the first motor 2 to firstly enter a set gear, then controlling the clutch 4 to be smoothly switched into the engine 1, and loading and driving the engine 1 after entering the gear, so that the smooth control process of gear shifting is completed.

Further, due to the synchronous control of the gear shifting of the first motor 2, the gear shifting time of the engine 1 is short, and in addition, due to the power compensation of the second motor 3 during the gear shifting, the sliding friction loading control of the clutch 4 is basically not needed during the gear shifting, so that the service life of the clutch 4 can be greatly prolonged, and the clutch 4 can even be free of maintenance for life. At traditional AMT, heavy manual transmission and based on P2's AMT hybrid transmission, it is difficult to overcome 4 slipping fatigue wear problems of clutch, and P23 hybrid system can improve the ride comfort of shifting by a wide margin, promotes the reliability of gearbox assembly. Because the synchronous control of bi-motor gear shifting, gear shifting mechanism mechanical reliability promotes, and the control degree of difficulty of stepping into of sliding sleeve of shifting reduces by a wide margin, and the quality of shifting far exceeds P2 thoughtlessly moves the framework. Especially in the sliding gear during climbing, the P23 hybrid motion can greatly improve the problem of shifting and slipping due to the shifting power compensation of the second motor 3, and the safety of the whole vehicle is improved.

It should be noted that the AMT is an automatic Transmission of an electronic control Mechanical type, and is fully assembled as an Automated Mechanical Transmission.

In a possible embodiment, the reverse gear function of the engine 1, in most cases, the reverse gear control of the vehicle can be realized by double-motor or single-motor driving. However, under some special working conditions, the electric quantity of a power battery is insufficient or the vehicle is continuously backed, the mechanical reverse gear function of the engine 1 becomes necessary, the P23 framework is specially matched with the mechanical reverse gear of the engine 1, the engine 1 is connected with the first motor 2 in parallel, the engine 1 or direct drive reverse gear control is carried out, the P2 and the P3 motors can be connected in parallel to provide reverse gear assistance, and the grade climbing of the reverse gear and the obstacle crossing reverse gear capability of a hollow area are improved.

In some possible embodiments of the invention, as shown in fig. 3 and 4, the gear assembly further comprises: an eleventh gear pair 80, a twelfth gear pair 81, a thirteenth gear pair 82, a fourteenth gear pair 83, and a fifteenth gear pair 84; the eleventh gear pair 80 is connected to the first input shaft 10 and the first intermediate shaft 40, respectively, and is disposed corresponding to the first gear shift mechanism K1 to realize switching among a plurality of gears; the twelfth gear pair 81 is connected to the first input shaft 10 and the first intermediate shaft 40, and is disposed corresponding to the first gear shift mechanism K1, so as to implement switching between multiple gears; the thirteenth gear pair 82 is disposed outside the output shaft 60 and the first intermediate shaft 40, respectively, and corresponds to the third gear shift mechanism K3, so as to realize switching among a plurality of gears; the fourteenth gear pair 83 is connected to the output shaft 60 and the first intermediate shaft 40, respectively, and is disposed corresponding to the fourth gear shift mechanism K4, so as to realize switching among a plurality of gears; the fifteenth gear pair 84 is connected to the output shaft 60 and the first countershaft 40, respectively, and is provided corresponding to the fourth gear shift mechanism K4 to achieve switching between a plurality of gears.

Specifically, the present embodiment provides an embodiment of the eleventh, twelfth, thirteenth, fourteenth and fifteenth gear pairs 80, 81, 82, 83 and 84, and the eleventh, twelfth, thirteenth, fourteenth and fifteenth gear pairs 81, 82, 83 and 84 are provided to switch the output shaft 60 among a plurality of gears.

In some possible embodiments of the invention, the gear assembly further comprises: sixteenth gear pair 85, seventeenth gear pair 86 and eighteenth gear pair 87; the sixteenth gear pair 85 is respectively connected with the first input shaft 10 and the second intermediate shaft 50 and is arranged between the first gear shifting mechanism K1 and the second gear shifting mechanism K2 to realize the switching among a plurality of gears; the seventeenth gear pair 86 is connected to the output shaft 60 and the second intermediate shaft 50, and is disposed corresponding to the second shift mechanism K2, so as to switch between multiple gears; the eighteenth gear pair 87 is connected to the output shaft 60 and the second intermediate shaft 50, respectively, and is provided corresponding to the third shift mechanism K3 to realize switching between a plurality of gears.

Specifically, the present embodiment provides an embodiment of the sixteenth gear pair 85, the seventeenth gear pair 86 and the eighteenth gear pair 87, and the sixteenth gear pair 85, the seventeenth gear pair 86 and the eighteenth gear pair 87 are provided, so that the first input shaft 10 and the second intermediate shaft 50, and the output shaft 60 and the second intermediate shaft 50 are switched among a plurality of gears.

In an application scenario, as shown in fig. 3 and 4, the engine 19 is used for a transmission path, wherein the engine 1 is involved in driving, the clutch 4 is closed, the four gear shifting mechanisms realize 9-gear shifting control, the engine 1 can be directly driven with high efficiency in the ninth gear, and the transmission path is simplest; when the engine 1 and the first motor 2 are driven in parallel at a third gear G3, a sixth gear G6 and a ninth gear G9, the second motor 3 can be out of gear and stopped, so that the efficient direct-drive function of the engine 1 under the cruising working condition is realized, and the efficient direct-drive function is as follows:

the transmission path of the first gear G1 of the engine 1 is: the engine 1 → the clutch 4 → the first input shaft 10 → the first shift mechanism K1 → the eleventh gear pair 80 → the first intermediate shaft 40 → the fifteenth gear pair 84 → the fourth shift mechanism K4 → the output shaft 60.

The transmission path of the second gear G2 of the engine 1 is: the engine 1 → the clutch 4 → the first input shaft 10 → the first shift mechanism K1 → the twelfth gear pair 81 → the first intermediate shaft 40 → the fifteenth gear pair 84 → the fourth shift mechanism K4 → the output shaft 60.

The transmission path of the third gear G3 of the engine 1 is: the engine 1 → the clutch 4 → the first input shaft 10 → the sixteenth gear pair 85 → the second intermediate shaft 50 → the eighteenth gear pair 87 → the third shift mechanism K3 → the output shaft 60.

The transmission path of the fourth gear G4 of the engine 1 is: the engine 1 → the clutch 4 → the first input shaft 10 → the first shift mechanism K1 → the eleventh gear pair 80 → the first intermediate shaft 40 → the fourteenth gear pair 83 → the fourth shift mechanism K4 → the output shaft 60.

The transmission path of the fifth gear G5 of the engine 1 is: the engine 1 → the clutch 4 → the first input shaft 10 → the first shift mechanism K1 → the twelfth gear pair 81 → the first intermediate shaft 40 → the fourteenth gear pair 83 → the fourth shift mechanism K4 → the output shaft 60.

The transmission path of the sixth gear G6 of the engine 1 is: the engine 1 → the clutch 4 → the first input shaft 10 → the sixteenth gear pair 85 → the second intermediate shaft 50 → the seventeenth gear pair 86 → the second shift mechanism K2 → the output shaft 60.

The transmission path of the seventh gear G7 of the engine 1 is: engine 1 → clutch 4 → first input shaft 10 → first shift mechanism K1 → eleventh gear pair 80 → first intermediate shaft 40 → thirteenth gear pair 82 → third shift mechanism K3 → output shaft 60.

The transmission path of the eighth gear G8 of the engine 1 is: the engine 1 → the clutch 4 → the first input shaft 10 → the first shift mechanism K1 → the twelfth gear pair 81 → the first intermediate shaft 40 → the thirteenth gear pair 82 → the third shift mechanism K3 → the output shaft 60.

The transmission path of the ninth gear G9 of the engine 1 is: the engine 1 → the clutch 4 → the first input shaft 10 → the second shift mechanism K2 → the output shaft 60.

In one application scenario, as shown in fig. 3 and 4, the first electric machine 2 shares 9 gears of transmission stiffness, the clutch 4 is closed, and the first electric machine 2 and the engine 1 share 9 gears and are linked in parallel; the clutch 4 is opened, and the first motor 2 and the second motor 3 can be purely electrically driven together in 6 gears according to 9 gears, specifically as follows:

the transmission path of the first gear G1 of the first electric machine 2 is: the first electric motor 2 → the second input shaft 20 → the first gear pair 70 → the first input shaft 10 → the first shift mechanism K1 → the eleventh gear pair 80 → the first intermediate shaft 40 → the fifteenth gear pair 84 → the fourth shift mechanism K4 → the output shaft 60.

The transmission path of the second gear G2 of the first electric machine 2 is: the first electric motor 2 → the second input shaft 20 → the first gear pair 70 → the first input shaft 10 → the first shift mechanism K1 → the twelfth gear pair 81 → the first intermediate shaft 40 → the fifteenth gear pair 84 → the fourth shift mechanism K4 → the output shaft 60.

The transmission path of the third gear G3 of the first electric machine 2 is: the first electric motor 2 → the second input shaft 20 → the first gear pair 70 → the first input shaft 10 → the sixteenth gear pair 85 → the second intermediate shaft 50 → the eighteenth gear pair 87 → the third shift mechanism K3 → the output shaft 60.

The transmission path of the fourth gear G4 of the first electric machine 2 is: the first electric motor 2 → the second input shaft 20 → the first gear pair 70 → the first input shaft 10 → the first shift mechanism K1 → the eleventh gear pair 80 → the first intermediate shaft 40 → the fourteenth gear pair 83 → the fourth shift mechanism K4 → the output shaft 60.

The transmission path of the fifth gear G5 of the first electric machine 2 is: the first electric motor 2 → the second input shaft 20 → the first gear pair 70 → the first input shaft 10 → the first shift mechanism K1 → the twelfth gear pair 81 → the first intermediate shaft 40 → the fourteenth gear pair 83 → the fourth shift mechanism K4 → the output shaft 60.

The transmission path of the sixth gear G6 of the first electric machine 2 is: the first electric motor 2 → the second input shaft 20 → the first gear pair 70 → the first input shaft 10 → the sixteenth gear pair 85 → the second intermediate shaft 50 → the seventeenth gear pair 86 → the second shift mechanism K2 → the output shaft 60.

The transmission path of the seventh gear G7 of the first electric machine 2 is: the first electric motor 2 → the second input shaft 20 → the first gear pair 70 → the first input shaft 10 → the first shift mechanism K1 → the eleventh gear pair 80 → the first intermediate shaft 40 → the thirteenth gear pair 82 → the third shift mechanism K3 → the output shaft 60.

The transmission path of the eighth gear G8 of the first electric machine 2 is: the first electric motor 2 → the second input shaft 20 → the first gear pair 70 → the first input shaft 10 → the first shift mechanism K1 → the twelfth gear pair 81 → the first intermediate shaft 40 → the thirteenth gear pair 82 → the third shift mechanism K3 → the output shaft 60.

The transmission path of the ninth gear G9 of the first electric machine 2 is: the first motor 2 → the second input shaft 20 → the first gear pair 70 → the first input shaft 10 → the second shift mechanism K2 → the output shaft 60.

In one application scenario, as shown in fig. 3 and 4, the second electric machine 3 provides 6 gear transmission paths, the second electric machine 3 can be driven together with the engine 1 and/or the first electric machine 2 in the first gear G1, the third gear G3, the fourth gear G4, the sixth gear G6, the seventh gear G7 and the ninth gear G9, and the engine 1 and the first electric machine 2 can be driven independently of the second electric machine 3 in the third gear G3, the sixth gear G6 and the ninth gear G9, so as to provide the second electric machine 3 with a non-powered gear-shifting interruption shift, as follows:

the transmission path of the first gear G1 of the second electric machine 3 is: the second electric machine 3 → the third input shaft 30 → the second gear pair 71 → the first input shaft 10 → the first shift mechanism K1 → the eleventh gear pair 80 → the first intermediate shaft 40 → the fifteenth gear pair 84 → the fourth shift mechanism K4 → the output shaft 60.

The transmission path of the third gear G3 of the second electric machine 3 is: the second electric motor 3 → the third input shaft 30 → the second gear pair 71 → the first input shaft 10 → the sixteenth gear pair 85 → the second intermediate shaft 50 → the eighteenth gear pair 87 → the third shift mechanism K3 → the output shaft 60.

The transmission path of the fourth gear G4 of the second electric machine 3 is: the second electric motor 3 → the third input shaft 30 → the second gear pair 71 → the first input shaft 10 → the first shift mechanism K1 → the eleventh gear pair 80 → the first intermediate shaft 40 → the fourteenth gear pair 83 → the fourth shift mechanism K4 → the output shaft 60.

The transmission path of the sixth gear G6 of the second electric machine 3 is: the second electric motor 3 → the third input shaft 30 → the second gear pair 71 → the first input shaft 10 → the sixteenth gear pair 85 → the second intermediate shaft 50 → the seventeenth gear pair 86 → the second shift mechanism K2 → the output shaft 60.

The transmission path of the seventh gear G7 of the second electric machine 3 is: the second electric motor 3 → the third input shaft 30 → the second gear pair 71 → the first input shaft 10 → the first shift mechanism K1 → the eleventh gear pair 80 → the first intermediate shaft 40 → the thirteenth gear pair 82 → the third shift mechanism K3 → the output shaft 60.

The transmission path of the ninth gear G9 of the second electric machine 3 is: the second electric machine 3 → the third input shaft 30 → the second gear pair 71 → the first input shaft 10 → the second shift mechanism K2 → the output shaft 60.

In a possible embodiment, the pure electric drive function is adopted, the clutch 4 is opened, the engine 1 is stopped, and the first motor 2 and the second motor 3 can be driven in 9 gears and in 6 gears of the first gear G1, the third gear G3, the fourth gear G4, the sixth gear G6, the seventh gear G7 and the ninth gear G9 together in pure electric drive; since there is no reverse gear setting of the engine 1, the reverse gear function is achieved with the second electric machine 3 or dual electric machine drive. The first electric machine 2 can be driven independently and purely electrically in a third gear G3, a sixth gear G6 and a ninth gear G9, and the second electric machine 3 can be driven in a first gear G1, a fourth gear G4 or a seventh gear G7.

In a possible implementation mode, the series hybrid mode is adopted, the vehicle is frequently started and stopped under the low-load urban working condition, and the oil saving rate is high when the electric quantity of the vehicle-mounted power battery is insufficient. In the series hybrid mode, the clutch 4 is closed, the engine 1 and the first motor 2 are in out-of-gear linkage, the first motor 2 works in the rotating speed mode to provide negative torque, mechanical input power of the engine 1 is converted into electric energy, and the electric energy is connected in series to generate electricity to charge a power battery, or part of the electric energy is directly provided for a controller of the second motor 3 to directly drive wheels. The second electric machine 3 can be driven purely electrically in the first gear G1, the fourth gear G4 or the seventh gear G7 independently.

In some possible embodiments of the invention, as shown in fig. 5 and 6, the gear assembly further comprises: an eleventh gear pair 80, a twelfth gear pair 81, a thirteenth gear pair 82, a fourteenth gear pair 83, and a fifteenth gear pair 84; the eleventh gear pair 80 is connected to the first input shaft 10 and the first intermediate shaft 40, respectively, and is disposed corresponding to the first gear shift mechanism K1 to realize switching among a plurality of gears; the twelfth gear pair 81 is connected to the first input shaft 10 and the first intermediate shaft 40, respectively, and is disposed corresponding to the first gear shift mechanism K1 to realize switching among a plurality of gears; the thirteenth gear pair 82 is respectively arranged outside the output shaft 60 and the first intermediate shaft 40 and corresponds to the second gear shifting mechanism K2, so as to realize switching among a plurality of gears; the fourteenth gear pair 83 is connected to the output shaft 60 and the first intermediate shaft 40, and is disposed corresponding to the third gear shift mechanism K3, so as to realize switching among a plurality of gears; the fifteenth gear pair 84 is connected to the output shaft 60 and the first countershaft 40, respectively, and is disposed corresponding to the third gear shift mechanism K3 for switching among a plurality of gears.

In some possible embodiments of the invention, as shown in fig. 5 and 6, the gear assembly further comprises: sixteenth gear pair 85, seventeenth gear pair 86 and eighteenth gear pair 87; the sixteenth gear pair 85 is respectively connected with the first input shaft 10 and the second intermediate shaft 50 and is arranged between the first gear shifting mechanism K1 and the second gear shifting mechanism K2 to realize the switching among a plurality of gears; the seventeenth gear pair 86 is connected to the output shaft 60 and the second intermediate shaft 50, respectively, and is disposed corresponding to the fourth gear shift mechanism K4, so as to realize switching among a plurality of gears; the eighteenth gear pair 87 is connected to the output shaft 60 and the second intermediate shaft 50, respectively, and is provided corresponding to the fourth shift mechanism K4 to realize switching between a plurality of gears.

Specifically, the present embodiment provides an embodiment of the sixteenth gear pair 85, the seventeenth gear pair 86 and the eighteenth gear pair 87, and by providing the sixteenth gear pair 85, the seventeenth gear pair 86 and the eighteenth gear pair 87, the switching of the first input shaft 10 and the second intermediate shaft 50, and the output shaft 60 and the second intermediate shaft 50 between the plurality of gears is realized.

It should be noted that in fig. 5 and 6, the output gear positions of the first intermediate shaft 40 and the second intermediate shaft 50 are adjusted, so as to reduce the length of the first intermediate shaft 40 and ensure the safety and stability of the operation of the frame.

In an application scenario, as shown in fig. 5 and fig. 6, the engine 19 is used for a transmission path, wherein the engine 1 is involved in driving, the clutch 4 is closed, the four gear shifting mechanisms realize 9-gear shifting control, the engine 1 can be directly driven with high efficiency in the ninth gear, and the transmission path is simplest; when the engine 1 and the first motor 2 are driven in parallel at the third gear G3, the sixth gear G6 and the ninth gear G9, the second motor 3 can be out of gear and stopped, so that the efficient direct-drive function of the engine 1 under the cruising working condition is realized, and the method specifically comprises the following steps:

the transmission path of the first gear G1 of the engine 1 is: the engine 1 → the clutch 4 → the first input shaft 10 → the first shift mechanism K1 → the eleventh gear pair 80 → the first intermediate shaft 40 → the fifteenth gear pair 84 → the third shift mechanism K3 → the output shaft 60.

The transmission path of the second gear G2 of the engine 1 is: the engine 1 → the clutch 4 → the first input shaft 10 → the first shift mechanism K1 → the twelfth gear pair 81 → the first intermediate shaft 40 → the fifteenth gear pair 84 → the third shift mechanism K3 → the output shaft 60.

The transmission path of the third gear G3 of the engine 1 is: the engine 1 → the clutch 4 → the first input shaft 10 → the sixteenth gear pair 85 → the second intermediate shaft 50 → the eighteenth gear pair 87 → the fourth shift mechanism K4 → the output shaft 60.

The transmission path of the fourth gear G4 of the engine 1 is: engine 1 → clutch 4 → first input shaft 10 → first shift mechanism K1 → eleventh gear pair 80 → first intermediate shaft 40 → thirteenth gear pair 82 → second shift mechanism K2 → output shaft 60.

The transmission path of the fifth gear G5 of the engine 1 is: the engine 1 → the clutch 4 → the first input shaft 10 → the first shift mechanism K1 → the twelfth gear pair 81 → the first intermediate shaft 40 → the thirteenth gear pair 82 → the second shift mechanism K2 → the output shaft 60.

The transmission path of the sixth gear G6 of the engine 1 is: the engine 1 → the clutch 4 → the first input shaft 10 → the sixteenth gear pair 85 → the second intermediate shaft 50 → the seventeenth gear pair 86 → the fourth shift mechanism K4 → the output shaft 60.

The transmission path of the seventh gear G7 of the engine 1 is: the engine 1 → the clutch 4 → the first input shaft 10 → the first shift mechanism K1 → the eleventh gear pair 80 → the first intermediate shaft 40 → the fourteenth gear pair 83 → the third shift mechanism K3 → the output shaft 60.

The transmission path of the eighth gear G8 of the engine 1 is: the engine 1 → the clutch 4 → the first input shaft 10 → the first shift mechanism K1 → the twelfth gear pair 81 → the first intermediate shaft 40 → the fourteenth gear pair 83 → the third shift mechanism K3 → the output shaft 60.

In one application scenario, as shown in fig. 5 and fig. 6, the first electric machine 2 shares 9 gears of transmission forces, the clutch 4 is closed, and the first electric machine 2 and the engine 1 share 9 gears and are linked in parallel; the clutch 4 is opened, and the first motor 2 and the second motor 3 can be purely electrically driven together in 6 gears according to 9 gears, specifically as follows:

the transmission path of the first gear G1 of the first electric machine 2 is: the first electric motor 2 → the second input shaft 20 → the first gear pair 70 → the first input shaft 10 → the first shift mechanism K1 → the eleventh gear pair 80 → the first intermediate shaft 40 → the fifteenth gear pair 84 → the third shift mechanism K3 → the output shaft 60.

The transmission path of the second gear G2 of the first electric machine 2 is: the first electric machine 2 → the second input shaft 20 → the first gear pair 70 → the first input shaft 10 → the first shift mechanism K1 → the twelfth gear pair 81 → the first intermediate shaft 40 → the fifteenth gear pair 84 → the third shift mechanism K3 → the output shaft 60.

The transmission path of the third gear G3 of the first electric machine 2 is: the first electric machine 2 → the second input shaft 20 → the first gear pair 70 → the first input shaft 10 → the sixteenth gear pair 85 → the second intermediate shaft 50 → the eighteenth gear pair 87 → the fourth shift mechanism K4 → the output shaft 60.

The transmission path of the fourth gear G4 of the first electric machine 2 is: the first electric machine 2 → the second input shaft 20 → the first gear pair 70 → the first input shaft 10 → the first shift mechanism K1 → the eleventh gear pair 80 → the first intermediate shaft 40 → the thirteenth gear pair 82 → the second shift mechanism K2 → the output shaft 60.

The transmission path of the fifth gear G5 of the first electric machine 2 is: the first electric machine 2 → the second input shaft 20 → the first gear pair 70 → the first input shaft 10 → the first shift mechanism K1 → the twelfth gear pair 81 → the first intermediate shaft 40 → the thirteenth gear pair 82 → the second shift mechanism K2 → the output shaft 60.

The transmission path of the sixth gear G6 of the first electric machine 2 is: the first electric motor 2 → the second input shaft 20 → the first gear pair 70 → the first input shaft 10 → the sixteenth gear pair 85 → the second intermediate shaft 50 → the seventeenth gear pair 86 → the fourth shift mechanism K4 → the output shaft 60.

The transmission path of the seventh gear G7 of the first electric machine 2 is: the first electric motor 2 → the second input shaft 20 → the first gear pair 70 → the first input shaft 10 → the first shift mechanism K1 → the eleventh gear pair 80 → the first intermediate shaft 40 → the fourteenth gear pair 83 → the third shift mechanism K3 → the output shaft 60.

The transmission path of the eighth gear G8 of the first electric machine 2 is: the first electric motor 2 → the second input shaft 20 → the first gear pair 70 → the first input shaft 10 → the first shift mechanism K1 → the twelfth gear pair 81 → the first intermediate shaft 40 → the fourteenth gear pair 83 → the third shift mechanism K3 → the output shaft 60.

In one application scenario, as shown in fig. 5 and 6, the second electric machine 3 provides 6 gear transmission paths, the second electric machine 3 can be driven together with the engine 1 and/or the first electric machine 2 in the first gear G1, the third gear G3, the fourth gear G4, the sixth gear G6, the seventh gear G7 and the ninth gear G9, and the engine 1 and the first electric machine 2 can be driven independently of the second electric machine 3 in the third gear G3, the sixth gear G6 and the ninth gear G9, so as to provide the second electric machine 3 with a non-powered gear-shifting interruption shift, as follows:

the transmission path of the first gear G1 of the second electric machine 3 is: the second electric motor 3 → the third input shaft 30 → the second gear pair 71 → the first input shaft 10 → the first shift mechanism K1 → the eleventh gear pair 80 → the first intermediate shaft 40 → the fifteenth gear pair 84 → the third shift mechanism K3 → the output shaft 60.

The transmission path of the third gear G3 of the second electric machine 3 is: the second electric motor 3 → the third input shaft 30 → the second gear pair 71 → the first input shaft 10 → the sixteenth gear pair 85 → the second intermediate shaft 50 → the eighteenth gear pair 87 → the fourth shift mechanism K4 → the output shaft 60.

The transmission path of the fourth gear G4 of the second electric machine 3 is: the second electric motor 3 → the third input shaft 30 → the second gear pair 71 → the first input shaft 10 → the first shift mechanism K1 → the eleventh gear pair 80 → the first intermediate shaft 40 → the thirteenth gear pair 82 → the second shift mechanism K2 → the output shaft 60.

The transmission path of the sixth gear G6 of the second electric machine 3 is: the second electric motor 3 → the third input shaft 30 → the second gear pair 71 → the first input shaft 10 → the sixteenth gear pair 85 → the second intermediate shaft 50 → the seventeenth gear pair 86 → the fourth shift mechanism K4 → the output shaft 60.

The transmission path of the seventh gear G7 of the second electric machine 3 is: the second electric motor 3 → the third input shaft 30 → the second gear pair 71 → the first input shaft 10 → the first shift mechanism K1 → the eleventh gear pair 80 → the first intermediate shaft 40 → the fourteenth gear pair 83 → the third shift mechanism K3 → the output shaft 60.

In some embodiments of the present invention, the present disclosure provides a working machine having the above-described two-motor hybrid transmission.

In a possible embodiment, the work machine is a vehicle.

In a possible embodiment, the work machine is a heavy-duty vehicle.

In a possible embodiment, the work machine is a medium load vehicle.

In a possible embodiment, the work machine is a light-duty vehicle.

In the description of the embodiments of the present invention, it should be noted that, unless explicitly stated or limited otherwise, the terms "connected" and "connected" are to be interpreted broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; may be directly connected or indirectly connected through an intermediate. Specific meanings of the above terms in the embodiments of the present invention can be understood by those of ordinary skill in the art according to specific situations.

Finally, it should be noted that: the above embodiments are merely illustrative of the present invention and are not to be construed as limiting the invention. Although the present invention has been described in detail with reference to the embodiments, it should be understood by those skilled in the art that various combinations, modifications and equivalents may be made to the technical solution of the present invention without departing from the spirit and scope of the technical solution of the present invention, and the technical solution of the present invention is covered by the claims of the present invention.

Claims

1. The utility model provides a bi-motor hybrid transmission case which characterized in that includes: the gear shifting mechanism comprises an engine (1), a first motor (2), a second motor (3), a first input shaft (10), a second input shaft (20), a third input shaft (30), a first intermediate shaft (40), a second intermediate shaft (50), a gear assembly, a first gear shifting mechanism (K1), a second gear shifting mechanism (K2), a third gear shifting mechanism (K3), a fourth gear shifting mechanism (K4) and an output shaft (60);

the first input shaft (10) is connected with the engine (1), the second input shaft (20) is connected with the first motor (2), and the third input shaft (30) is connected with the second motor (3);

the second input shaft (20), the third input shaft (30), the first intermediate shaft (40) and the second intermediate shaft (50) are arranged in parallel with the first input shaft (10), respectively;

the gear assemblies are arranged on the first input shaft (10), the second input shaft (20), the third input shaft (30), the first intermediate shaft (40), the second intermediate shaft (50) and the output shaft (60);

the first input shaft (10) is selectively coupled to the first shift mechanism (K1) and the second shift mechanism (K2), respectively, and selectively coupled to the third shift mechanism (K3) and the fourth shift mechanism (K4), respectively, via the first countershaft (40) and the second countershaft (50);

the second input shaft (20) and the third input shaft (30) are selectively coupled to the first shift mechanism (K1) and selectively coupled to the second shift mechanism (K2), the third shift mechanism (K3), and the fourth shift mechanism (K4) via the first countershaft (40) and the second countershaft (50);

the output shaft (60) is selectively linked with the first input shaft (10) and/or the second input shaft (20) and/or the third input shaft (30) through the first gear shifting mechanism (K1), the second gear shifting mechanism (K2), the third gear shifting mechanism (K3) and the fourth gear shifting mechanism (K4) respectively so as to realize the switching among a plurality of gears;

wherein the first and second gear shift mechanisms (K1, K2) are arranged on the first input shaft (10);

the third gear shifting mechanism (K3) and the fourth gear shifting mechanism (K4) are arranged on the output shaft (60).

2. The dual-motor hybrid transmission of claim 1, further comprising: the clutch (4) is respectively connected with a power shaft of the engine (1) and the first input shaft (10) so as to realize selectable linkage between the engine (1) and the first input shaft (10).

3. The double-motor hybrid transmission according to claim 1, characterized in that at least two of said first intermediate shafts (40) are uniformly arranged around the circumference of said first input shaft (10);

and/or at least two second intermediate shafts (50) are uniformly distributed around the circumference of the first input shaft (10).

4. The dual-motor hybrid transmission of claim 1, wherein said gear assembly comprises: a first gear pair (70) and a second gear pair (71);

the first gear pair (70) is respectively connected with the first input shaft (10) and the second input shaft (20) so as to realize linkage of the first input shaft (10) and the second input shaft (20);

the second gear pair (71) is connected with the first input shaft (10) and the third input shaft (30) respectively and is arranged corresponding to the first gear shifting mechanism (K1) so as to realize switching among a plurality of gears.

5. The dual-motor hybrid transmission as defined in any one of claims 1 to 4, wherein said gear assembly further comprises: a third gear pair (72), a fourth gear pair (73), a fifth gear pair (74) and a sixth gear pair (75);

the third gear pair (72) is respectively connected with the first input shaft (10) and the first intermediate shaft (40) and is arranged corresponding to the first gear shifting mechanism (K1) so as to realize the switching among a plurality of gears;

the fourth gear pair (73) is respectively connected with the first input shaft (10) and the first intermediate shaft (40) and is arranged corresponding to the first gear shifting mechanism (K1) so as to realize switching among a plurality of gears;

the fifth gear pair (74) is respectively connected with the output shaft (60) and the first intermediate shaft (40) and is arranged corresponding to the fourth gear shifting mechanism (K4) so as to realize the switching among a plurality of gears;

the sixth gear pair (75) is connected with the output shaft (60) and the first intermediate shaft (40) respectively and is arranged corresponding to the fourth gear shifting mechanism (K4) so as to realize switching among a plurality of gears.

6. The dual-motor hybrid transmission of claim 5, wherein said gear assembly further comprises: a seventh gear pair (76), an eighth gear pair (77), a ninth gear pair (78) and a tenth gear pair (79);

the seventh gear pair (76) is connected with the first input shaft (10) and the second intermediate shaft (50) respectively and is arranged between the first gear shifting mechanism (K1) and the second gear shifting mechanism (K2) to realize the switching among a plurality of gears;

the eighth gear pair (77) is connected with the output shaft (60) and the second intermediate shaft (50) respectively and is arranged corresponding to the second gear shifting mechanism (K2) so as to realize switching among a plurality of gears;

the ninth gear pair (78) is connected with the output shaft (60) and the second intermediate shaft (50) respectively and is arranged corresponding to the third gear shifting mechanism (K3) so as to realize the switching among a plurality of gears;

the tenth gear pair (79) is connected with the output shaft (60) and the second intermediate shaft (50) respectively and is arranged corresponding to the third gear shifting mechanism (K3) so as to realize switching among a plurality of gears.

7. The double-motor hybrid transmission as claimed in claim 6, characterized in that said output shaft (60) and said second intermediate shaft (50) perform a plurality of gear shifts, including at least a reverse gear, through said tenth gear pair (79) and said third gear shift mechanism (K3).

8. The dual-motor hybrid transmission as defined in any one of claims 1 to 4, wherein said gear assembly further comprises: an eleventh gear pair (80), a twelfth gear pair (81), a thirteenth gear pair (82), a fourteenth gear pair (83) and a fifteenth gear pair (84);

the eleventh gear pair (80) is respectively connected with the first input shaft (10) and the first intermediate shaft (40) and is arranged corresponding to the first gear shifting mechanism (K1) so as to realize switching among a plurality of gears;

the twelfth gear pair (81) is connected with the first input shaft (10) and the first intermediate shaft (40) respectively and is arranged corresponding to the first gear shifting mechanism (K1) so as to realize switching among a plurality of gears;

the thirteenth gear pair (82) is respectively arranged outside the output shaft (60) and the first intermediate shaft (40) and corresponds to the third gear shifting mechanism (K3) so as to realize the switching among a plurality of gears;

the fourteenth gear pair (83) is connected with the output shaft (60) and the first intermediate shaft (40) respectively and is arranged corresponding to the fourth gear shifting mechanism (K4) so as to realize switching among a plurality of gears;

the fifteenth gear pair (84) is connected with the output shaft (60) and the first intermediate shaft (40) respectively and is arranged corresponding to the fourth gear shifting mechanism (K4) so as to realize switching among a plurality of gears.

9. The dual-motor hybrid transmission of claim 8, wherein said gear assembly further comprises: a sixteenth gear pair (85), a seventeenth gear pair (86), and an eighteenth gear pair (87);

the sixteenth gear pair (85) is respectively connected with the first input shaft (10) and the second intermediate shaft (50) and is arranged between the first gear shifting mechanism (K1) and the second gear shifting mechanism (K2) so as to realize switching among a plurality of gears;

the seventeenth gear pair (86) is connected with the output shaft (60) and the second intermediate shaft (50) respectively and is arranged corresponding to the second gear shifting mechanism (K2) so as to realize the switching among a plurality of gears;

and the eighteenth gear pair (87) is respectively connected with the output shaft (60) and the second intermediate shaft (50) and is arranged corresponding to the third gear shifting mechanism (K3) so as to realize the switching among a plurality of gears.

10. The dual-motor hybrid transmission as defined in any one of claims 1 to 4, wherein said gear assembly further comprises: an eleventh gear pair (80), a twelfth gear pair (81), a thirteenth gear pair (82), a fourteenth gear pair (83) and a fifteenth gear pair (84);

the thirteenth gear pair (82) is respectively arranged outside the output shaft (60) and the first intermediate shaft (40) and corresponds to the second gear shifting mechanism (K2) so as to realize the switching among a plurality of gears;

the fourteenth gear pair (83) is connected with the output shaft (60) and the first intermediate shaft (40) respectively and is arranged corresponding to the third gear shifting mechanism (K3) so as to realize switching among a plurality of gears;

the fifteenth gear pair (84) is connected with the output shaft (60) and the first intermediate shaft (40) respectively and is arranged corresponding to the third gear shifting mechanism (K3) so as to realize switching among a plurality of gears.

11. The dual-motor hybrid transmission of claim 10, wherein said gear assembly further comprises: a sixteenth gear pair (85), a seventeenth gear pair (86) and an eighteenth gear pair (87);

the sixteenth gear pair (85) is respectively connected with the first input shaft (10) and the second intermediate shaft (50) and is arranged between the first gear shifting mechanism (K1) and the second gear shifting mechanism (K2) to realize the switching among a plurality of gears;

the seventeenth gear pair (86) is connected with the output shaft (60) and the second intermediate shaft (50) respectively and is arranged corresponding to the fourth gear shifting mechanism (K4) so as to realize the switching among a plurality of gears;

and the eighteenth gear pair (87) is respectively connected with the output shaft (60) and the second intermediate shaft (50) and is arranged corresponding to the fourth gear shifting mechanism (K4) so as to realize the switching among a plurality of gears.

12. A working machine having the two-motor hybrid transmission according to any one of claims 1 to 11.