CN109139877B - Speed change system of EMT gearbox - Google Patents

Speed change system of EMT gearbox Download PDF

Info

Publication number
CN109139877B
CN109139877B CN201811109009.0A CN201811109009A CN109139877B CN 109139877 B CN109139877 B CN 109139877B CN 201811109009 A CN201811109009 A CN 201811109009A CN 109139877 B CN109139877 B CN 109139877B
Authority
CN
China
Prior art keywords
gear
output shaft
gearbox
motor
power
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
CN201811109009.0A
Other languages
Chinese (zh)
Other versions
CN109139877A (en
Inventor
李雪原
汪磊
周俊杰
张艳松
裴伟亚
李世超
王郓
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Beijing Institute of Technology BIT
Original Assignee
Beijing Institute of Technology BIT
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Beijing Institute of Technology BIT filed Critical Beijing Institute of Technology BIT
Priority to CN201811109009.0A priority Critical patent/CN109139877B/en
Publication of CN109139877A publication Critical patent/CN109139877A/en
Application granted granted Critical
Publication of CN109139877B publication Critical patent/CN109139877B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)
  • Hybrid Electric Vehicles (AREA)

Abstract

The invention provides a speed change system of an EMT gearbox, which comprises an engine, a clutch, a motor, a planetary reducer and a gearbox, wherein the clutch is installed on the internal output end of the engine, the engine is connected with the motor through the clutch, the motor is positioned outside the engine, and the motor is connected with the gearbox through the planetary reducer. The invention reduces the volume of the gearbox, simplifies the structure of the gearbox to a certain extent, reduces the manufacturing cost and greatly improves the dynamic property of the automobile when climbing a slope.

Description

Speed change system of EMT gearbox
Technical Field
The invention belongs to the technical field of application of gearboxes, and particularly relates to a speed changing system of an EMT gearbox.
Background
The performance of an automobile is greatly influenced by a gearbox and an engine, the dynamic property and the economical efficiency are important indexes for evaluating the performance of the automobile, the requirement on climbing is high for the automobile such as a tank and the like which runs under the condition of non-roads, generally, in order to improve the climbing performance of the automobile, a ten-gear transmission is designed in the conventional gearbox, a plurality of gear sets such as the ten-gear transmission are generally adopted, the volume and the mass of the gearbox are increased due to the increase of the gear sets, the manufacturing cost is high, the maintenance is difficult, the price is high, and meanwhile, the transmission ratio of the gearbox is not greatly improved.
Disclosure of Invention
Aiming at the problems in the prior art, the invention provides a speed changing system of an EMT gearbox, which solves the problems of high manufacturing cost, high quality, large volume and the like of the gearbox in the prior art. The technical scheme of the invention is as follows:
an EMT gearbox comprises an engine, a clutch, a motor, a planetary reducer and a gearbox, wherein the clutch is mounted at the inner output end of the engine, the engine is connected with the motor through the clutch, the motor is located outside the engine, and the motor is connected with the gearbox through the planetary reducer;
a gearbox system is improved on an intermediate shaft type transmission, a constant mesh gear and the rear end of a shaft of the transmission are integrated, a bearing support at the front end of a second shaft (an output shaft) is arranged in a hole at the rear end of a first shaft (an input shaft), the axes of the two shafts are on the same straight line, an intermediate shaft is arranged in parallel with the first shaft and the second shaft, each gear is driven by the constant mesh gear, and a gear shifting mechanism adopts a mesh sleeve for gear shifting; the transmission system is characterized in that a climbing gear connected with a first gear is sleeved on an output shaft in an empty mode, a meshing sleeve is connected with the left side to form a first gear ratio and is transmitted to a planet row mechanism rightwards, the first gear ratio is input into a planet carrier through a sun gear and is transmitted to the output shaft through a right meshing sleeve, and the climbing gear transmission ratio is obtained;
the gearbox system comprises the following six gears:
(1) first gear power transmission route: power is from engine 1, clutch 2, through motor 3 again, and one-level planet row reduction gear 4 transmits the jackshaft through the constant mesh gear train to the jackshaft, and first gear gearset combines together with meshing cover Z12 for the empty first gear that overlaps on the output shaft is fixed in on the output shaft, and power is through the first gear gearset speed reduction transmission to the output shaft, and the speed reduction is passed through twice in the gearbox this moment, and first gear drive ratio is in the gearbox:
Figure BDA0001808598830000021
(2) second gear power transmission route: power is from engine 1, clutch 2, through motor 3 again, and one-level planet row reduction gear 4 transmits the jackshaft through the constant mesh gear train, and second gear set Z22 combines together with second, third gear meshing cover for the second gear of empty cover on the output shaft is fixed in on the output shaft, and power passes through second gear set speed reduction and transmits to the output shaft, and through twice speed reductions in the gearbox, second gear drive ratio is in the gearbox:
Figure BDA0001808598830000022
(3) third gear power transmission route: the power is from engine 1, clutch 2, through motor 3 again, and one-level planet row reduction gear 4 transmits the jackshaft through the constant mesh gear train, and third gear set Z32 combines together with second, third gear meshing cover for the third gear that the free overlaps on the output shaft is fixed in on the output shaft, and power passes through the third gear set speed reduction and transmits to the output shaft, and the reduction is twice in the gearbox:
Figure BDA0001808598830000023
(4) a fourth gear power transmission route: the power is from engine 1, clutch 2, and then through the electrical machinery 3, the first-class planet arranges the speed reducer 4, the bearing support of front end of second shaft in the first shaft rear end is connected with second shaft (output shaft), the fourth, fifth gear engaging sleeve is connected with input shaft, the power is transmitted to the output shaft directly from the input shaft, there is not deceleration in the change-speed gear box, the drive ratio is 1;
(5) a fifth gear power transmission route: power is from engine 1, clutch 2, through motor 3 again, and one-level planet row reduction gear 4 transmits the jackshaft through the constant mesh gear train, and five-gear set Z52 combines together with four, five mesh sleeves for the empty five-gear who overlaps on the output shaft is fixed in on the output shaft, and power is through five-gear set speed reduction transmission to the output shaft, through twice speed reduction in the gearbox:
Figure BDA0001808598830000031
(6) climbing a slope: power is from engine 1, clutch 2, again through motor 3, one-level planet row reduction gear 4 transmits the jackshaft through the constant mesh gear set, combines together through planet gear set and grade meshing cover of climbing for the empty cover is fixed in on the output shaft at the epaxial first gear wheel of output, and power transmits the planet through a gear set and arranges the mechanism, through the planet row speed reduction transmission to the output shaft, through the cubic speed reduction in the gearbox, the drive ratio increase this moment, and the torque transmission increases, and the drive ratio is:
Figure BDA0001808598830000032
preferably, the low-voltage electrification of the controller of the motor is 24V consistent with that of the whole vehicle, and the high-voltage direct-current rated voltage is 550V.
Preferably, the gearbox is composed of a direct gear, a three-gear set, a first-gear set, a planetary gear set, a second first-gear set, a second gear set, a fifth-gear set, an input shaft, an output shaft and an intermediate shaft.
Preferably, the clutch is a wet clutch.
Preferably, the motor for the gearbox adopts a vehicle permanent magnet synchronous motor with high torque density.
Fig. 5 provides a power transmission output route of the climbing gear of the present invention, wherein power is input from an input shaft, passes through a normally meshed gear, a common gear set of a first gear and a planet row, and reaches an output shaft through a gear set of the planet row, in the gear set of the planet row, a gear ring is fixed, and is input from a sun gear and output from a planet carrier, and the transmission ratio is:
Figure BDA0001808598830000041
wherein n is2The rotating speed of an output shaft:
Figure BDA0001808598830000042
therefore, the total gear ratio of the climbing gear is as follows:
Figure BDA0001808598830000043
the invention has the beneficial effects that: the motor for the EMT gearbox adopts the vehicle permanent magnet synchronous motor with high torque density, the motor system has high efficiency and wide speed regulation range; the safety performance is good, the insulation level is H, the protection level is IP66, and a driver and a controller matched with the insulation level and the protection level are integrally designed, a CAN communication interface is adopted, and the controllability is high; the size of the gearbox is reduced, the structure of the gearbox is simplified to a certain extent, the manufacturing cost is reduced, and the dynamic property of the automobile in climbing is greatly improved.
Drawings
FIG. 1 is a schematic view of a linkage arrangement according to the present invention;
FIG. 2 is a diagrammatic view of the transmission of the present invention;
FIG. 3 illustrates the power transmission paths of the first, second, third and fifth gears of the present invention;
FIG. 4 is a fourth gear power transmission path of the present invention;
FIG. 5 is a power transmission route diagram of a grade climbing according to the present invention;
in the figure: 1. an engine; 2. a clutch; 3. an electric motor; 4. a planetary reducer; 5. a gearbox; 501. a direct gear; 502. a third gear gearset; 503. a first gear set; 504. a planetary gear set; 505. a second first gear gearset; 506. a second gear set; 507. a fifth gear set; 508. an input shaft; 509. an output shaft; 510. an intermediate shaft; 511. a first gear meshing sleeve; 512. a planetary gear mesh sleeve; 513. a third gear meshing sleeve; 514. five-gear meshing sleeve
Detailed Description
The present invention will now be described in further detail with reference to the following figures and specific examples, which are intended to be illustrative, but not limiting, of the invention.
Example 1
The embodiment provides an EMT gearbox, which comprises an engine 1, a clutch 2, a motor 3, a planetary reducer 4 and a gearbox 5, wherein the clutch 2 is installed on the inner output end of the engine 1, the engine 1 is connected with the motor 3 through the clutch 2, the motor 3 is located outside the engine 1, and the motor 3 is connected with the gearbox 5 through the planetary reducer 4;
a transmission system characterized by: the middle shaft type transmission is improved, a normally meshed gear is integrated with the rear end of a first shaft of the transmission, a front end bearing support of a second shaft (an output shaft) is arranged in a hole at the rear end of a first shaft (an input shaft), the axes of the two shafts are on the same straight line, a middle shaft is arranged in parallel with the first shaft and the second shaft, all gears are driven by the normally meshed gear, and a gear shifting mechanism is shifted by a meshed sleeve; the transmission system is characterized in that a climbing gear connected with a first gear is sleeved on an output shaft in an empty mode, a meshing sleeve is connected with the left side to form a first gear ratio and is transmitted to a planet row mechanism rightwards, the first gear ratio is input into a planet carrier through a sun gear and is transmitted to the output shaft through a right meshing sleeve, and the climbing gear transmission ratio is obtained;
the gearbox system comprises the following six gears:
(1) first gear power transmission route: power is from engine 1, clutch 2, through motor 3 again, and one-level planet row reduction gear 4 transmits the jackshaft through the constant mesh gear train to the jackshaft, and first gear gearset combines together with meshing cover Z12 for the empty first gear that overlaps on the output shaft is fixed in on the output shaft, and power is through the first gear gearset speed reduction transmission to the output shaft, and the speed reduction is passed through twice in the gearbox this moment, and first gear drive ratio is in the gearbox:
Figure BDA0001808598830000061
(2) second gear power transmission route: power is from engine 1, clutch 2, through motor 3 again, and one-level planet row reduction gear 4 transmits the jackshaft through the constant mesh gear train, and second gear set Z22 combines together with second, third gear meshing cover for the second gear of empty cover on the output shaft is fixed in on the output shaft, and power passes through second gear set speed reduction and transmits to the output shaft, and through twice speed reductions in the gearbox, second gear drive ratio is in the gearbox:
Figure BDA0001808598830000062
(3) third gear power transmission route: the power is transmitted from the engine 1, the clutch 2, the motor 3 and the primary planet row speed reducer 4 through the constant meshThe gear combination set is transmitted to the intermediate shaft, the third gear set Z32 is combined with the second gear meshing sleeve and the third gear meshing sleeve, so that a third gear which is sleeved on the output shaft in an empty way is fixed on the output shaft, power is transmitted to the output shaft through the third gear set in a speed reduction way, and the speed in the gearbox is reduced twice:
Figure BDA0001808598830000063
(4) a fourth gear power transmission route: the power is from engine 1, clutch 2, and then through the electrical machinery 3, the first-class planet arranges the speed reducer 4, the bearing support of front end of second shaft in the first shaft rear end is connected with second shaft (output shaft), the fourth, fifth gear engaging sleeve is connected with input shaft, the power is transmitted to the output shaft directly from the input shaft, there is not deceleration in the change-speed gear box, the drive ratio is 1;
(5) a fifth gear power transmission route: power is from engine 1, clutch 2, through motor 3 again, and one-level planet row reduction gear 4 transmits the jackshaft through the constant mesh gear train, and five-gear set Z52 combines together with four, five mesh sleeves for the empty five-gear who overlaps on the output shaft is fixed in on the output shaft, and power is through five-gear set speed reduction transmission to the output shaft, through twice speed reduction in the gearbox:
Figure BDA0001808598830000064
(6) climbing a slope: power is from engine 1, clutch 2, again through motor 3, one-level planet row reduction gear 4 transmits the jackshaft through the constant mesh gear set, combines together through planet gear set and grade meshing cover of climbing for the empty cover is fixed in on the output shaft at the epaxial first gear wheel of output, and power transmits the planet through a gear set and arranges the mechanism, through the planet row speed reduction transmission to the output shaft, through the cubic speed reduction in the gearbox, the drive ratio increase this moment, and the torque transmission increases, and the drive ratio is:
Figure BDA0001808598830000071
preferably, the low-voltage electrification of the controller of the motor 3 is 24V consistent with that of the whole vehicle, and the high-voltage direct-current rated voltage is 550V.
Preferably, the transmission 5 is composed of a direct gear 501, a third gear set 502, a first gear set 503, a planetary gear set 504, a second first gear set 505, a second gear set 506, a fifth gear set 507, an input shaft 508, an output shaft 509 and an intermediate shaft 510, and the gears are provided with a first gear meshing sleeve 511, a planetary gear meshing sleeve 512, a third gear meshing sleeve 513 and a fifth gear meshing sleeve 514.
Preferably, the clutch 2 is a wet clutch.
Preferably, the motor for the gearbox 5 is a vehicle permanent magnet synchronous motor with high torque density.
Example 2
The EMT transmission principle obtained in embodiment 1 is explained as follows:
the structure of the invention is that the engine 1, the clutch 2, the electric motor 3, the planetary reducer 4 and the gearbox 5 are arranged, in order to save the axial space, the clutch 2 adopts a wet clutch and is arranged in the motor, the clutch 2 is operated to complete combination and separation through a stepping motor, the stepping motor is arranged outside the motor and is connected through a reduction gear, the motor for the EMT gearbox adopts a vehicle permanent magnet synchronous motor with high torque density, the efficiency of the motor system is high, and the speed regulation range is wide; the safety performance is good, insulation level H, protection level IP66, and driver and controller that match are as an organic whole design, adopt CAN communication interface, and the controllability is high. The low-voltage electrification of the motor controller is 24V consistent with that of the whole vehicle, and the high-voltage direct-current rated voltage is 550V.
Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention, and that variations, modifications, substitutions and alterations can be made to the above embodiments by those of ordinary skill in the art within the scope of the present invention.

Claims (5)

1. A variable speed system of an EMT gearbox comprises an engine (1), a clutch (2), a motor (3), a planetary reducer (4) and a gearbox (5), and is characterized in that: the clutch (2) is mounted on the inner output end of the engine (1), the engine (1) is connected with the motor (3) through the clutch (2), the motor (3) is located outside the engine (1), and the motor (3) is connected with the gearbox (5) through the planetary reducer (4); the method is characterized in that: the hole at the rear end of the input shaft is internally provided with an output shaft front end bearing support, the axes of the two shafts are on the same straight line, the intermediate shaft is arranged in parallel with the input shaft and the output shaft, and each gear is driven by a normally meshed gear; the gearbox system comprises the following six gears:
(1) first gear power transmission route: power is from engine (1), clutch (2), again through motor (3), one-level planet row reduction gear (4) through constant mesh gear train transmission to jackshaft, and the second gear in the first gear train combines together with a gear meshing cover for the fourth gear of empty cover in the first gear train on the output shaft is fixed in on the output shaft, and power is through a gear train speed reduction transmission to the output shaft, and through twice speed reductions in the gearbox this moment, a gear drive ratio is in the gearbox:
Figure FDA0002681102130000011
wherein Zc1 represents the number of teeth of the first gear, and Zc2 represents the number of teeth of the second gear; zp1 represents the number of teeth of the first gear in the first gear set; zp2 represents the number of teeth on the second gear of the first gear set;
(2) second gear power transmission route: power is from engine (1), clutch (2), again through motor (3), and one-level planet row reduction gear (4) transmit the jackshaft through the constant mesh gear train, and fourth gear in the second gear train combines together with second, third gear meshing cover for the second gear of empty cover in the second gear train on the output shaft is fixed in on the output shaft, and power is through the second gear reduction of gear train transmission to the output shaft, through two reductions in the gearbox, and second gear drive ratio is in the gearbox:
Figure FDA0002681102130000012
wherein Z21 represents the tooth count of the first gear in the second gear set; z22 represents the tooth count for the second gear of the second gear set;
(3) third gear power transmission route: power is from engine (1), clutch (2), through motor (3) again, and one-level planet row reduction gear (4) transmit the jackshaft through the constant mesh gear set, and the second gear in the third gear cluster combines together with second, third gear meshing cover for the second gear of the third gear cluster of empty cover on the output shaft is fixed in on the output shaft, and power passes through the third gear cluster and slows down the speed and transmit to the output shaft, through twice in the gearbox:
Figure FDA0002681102130000013
wherein Z31 represents the tooth count of the first gear in the third gear set; z32 represents the tooth count for the second gear of the third gear set;
(4) a fourth gear power transmission route: the power is from the engine (1), clutch (2), and then through the electrical machinery (3), the first grade planet arranges the speed reducer (4), the bearing support of front end of output shaft in the rear end of input shaft is connected with output shaft, the fourth, fifth gear engaging sleeve is connected with input shaft, the power is transmitted to the output shaft directly from the input shaft, there is not deceleration in the change-speed gear box, the drive ratio is 1;
(5) a fifth gear power transmission route: power is from engine (1), clutch (2), through motor (3) again, and one-level planet row reduction gear (4) transmit the jackshaft through constant mesh gear set, and the second gear in the five-gear set combines together with four, five-gear meshing cover for the second gear of empty cover in the five-gear set on the output shaft is fixed in on the output shaft, and power is through five-gear set speed reduction transmission to the output shaft, through twice speed reductions in the gearbox:
Figure FDA0002681102130000021
wherein Z51 represents the tooth count of the first gear in the fifth gear set; z52 represents the tooth count for the second gear of the fifth gear set;
(6) climbing a slope: power is from engine (1), clutch (2), again through motor (3), one-level planet row reduction gear (4) transmit the jackshaft through the constant mesh gear train, planet carrier through the planet row in the planet row gear train combines together with planet row gear meshing cover, make the planet row gear train of empty cover on the output shaft be fixed in on the output shaft, power transmits the planet through a gear train and arranges the mechanism, the rethread planet row slows down and transmits the output shaft, through the cubic speed reduction in the gearbox, the drive ratio increases this moment, the torque transmission increases, the drive ratio is:
Figure FDA0002681102130000022
where Zq2 represents the number of teeth in the planet; zt2 represents the number of teeth on the sun gear.
2. The transmission system of an EMT gearbox according to claim 1, wherein: the low-voltage electrification of a controller of the motor (3) is consistent with that of the whole vehicle and is 24V, and the high-voltage direct-current rated voltage is 550V.
3. The transmission system of an EMT gearbox according to claim 1, wherein: the gearbox (5) is composed of a direct gear (501), a third gear set (502), a first gear set (503), a planetary gear set (504), a second gear set (506), a fifth gear set (507), an input shaft (508), an output shaft (509) and an intermediate shaft (510), and a first gear meshing sleeve (511), a planetary gear meshing sleeve (512), a second gear meshing sleeve and a third gear meshing sleeve (513) and a fourth gear meshing sleeve and a fifth gear meshing sleeve (514) are arranged on the output shaft.
4. The transmission system of an EMT gearbox according to claim 1, wherein: the clutch (2) adopts a wet clutch.
5. The transmission system of an EMT gearbox according to claim 1, wherein: the motor for the gearbox (5) adopts a vehicle permanent magnet synchronous motor with high torque density.
CN201811109009.0A 2018-09-21 2018-09-21 Speed change system of EMT gearbox Active CN109139877B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201811109009.0A CN109139877B (en) 2018-09-21 2018-09-21 Speed change system of EMT gearbox

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201811109009.0A CN109139877B (en) 2018-09-21 2018-09-21 Speed change system of EMT gearbox

Publications (2)

Publication Number Publication Date
CN109139877A CN109139877A (en) 2019-01-04
CN109139877B true CN109139877B (en) 2020-12-25

Family

ID=64823434

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201811109009.0A Active CN109139877B (en) 2018-09-21 2018-09-21 Speed change system of EMT gearbox

Country Status (1)

Country Link
CN (1) CN109139877B (en)

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4129290C1 (en) * 1991-09-03 1993-02-25 Mercedes-Benz Aktiengesellschaft, 7000 Stuttgart, De
SE518332C2 (en) * 2001-02-12 2002-09-24 Volvo Lastvagnar Ab Power units for motor vehicles
CN2835710Y (en) * 2005-10-21 2006-11-08 山东福田重工股份有限公司 Transmission case with 10+10 gear positions
WO2008124001A1 (en) * 2007-04-06 2008-10-16 Borgwarner Inc. Dual clutch transmission
SE535764C2 (en) * 2011-04-18 2012-12-11 Scania Cv Ab Gearbox and a method of connecting an optional equipment via the gearbox
DE102013226529A1 (en) * 2013-12-18 2015-06-18 Zf Friedrichshafen Ag Gearbox in countershaft design
CN105909734A (en) * 2016-06-22 2016-08-31 陕西法士特齿轮有限责任公司 Multi-reverse-gear transmission

Also Published As

Publication number Publication date
CN109139877A (en) 2019-01-04

Similar Documents

Publication Publication Date Title
CN100400928C (en) Four branch differential transmission systems.
US8226514B2 (en) Multi-speed transmission with axis transfer
CN102490585A (en) Automobile hybrid power assembly
US20110021300A1 (en) Multi-speed transmission with multi-axis transfer
CN108528185B (en) Longitudinally-arranged multi-gear electric driving power assembly
CN109318704B (en) Electric drive transmission device
CN103066748A (en) Integrated two-gear motor transmission for pure electric vehicle
CN106004407A (en) Hybrid electric drive assembly and vehicle with same
US8881614B2 (en) Vehicle transmissions
CN103758947A (en) Mechanical three-shaft type high-speed-ratio automobile gearbox
CN101311580A (en) 8-gear transmission
CN110774881A (en) Double-motor hybrid power module structure
CN202349119U (en) Double-clutch transmission for tractor
CN214274373U (en) Commercial transmission of new forms of energy electricelectric motor
CN114043866A (en) Power transmission system and vehicle with same
CN109578533B (en) Three-gear electric assembly and speed ratio determination method thereof
CN109139877B (en) Speed change system of EMT gearbox
CN211918383U (en) Longitudinally-arranged two-gear integrated electric drive bridge behind motor
CN205800774U (en) A kind of hybrid power drive assembly and be provided with the automobile of this assembly
CN210454446U (en) Hybrid power transmission device
CN201836312U (en) Arrangement structure of gear shaft system of gear box
CN204572953U (en) Share the two intermediate-shaft speed changing box of non-equidistant of input shaft gear
CN114165563A (en) Longitudinal rear-drive hybrid transmission structure
CN110778679A (en) Dual-motor and shafting arrangement structure of hybrid power transmission
CN105291807A (en) Driving device of hybrid vehicle

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination
GR01 Patent grant
GR01 Patent grant