CN110001371B - Opposite type double-motor power coupling automatic transmission - Google Patents

Opposite type double-motor power coupling automatic transmission Download PDF

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Publication number
CN110001371B
CN110001371B CN201910321095.XA CN201910321095A CN110001371B CN 110001371 B CN110001371 B CN 110001371B CN 201910321095 A CN201910321095 A CN 201910321095A CN 110001371 B CN110001371 B CN 110001371B
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China
Prior art keywords
gear
bevel gear
motor
transmission
driving motor
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CN201910321095.XA
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Chinese (zh)
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CN110001371A (en
Inventor
洪亮
李晓炜
张庆永
高万青
吴勇志
陈泉发
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Fujian University of Technology
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Fujian University of Technology
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Priority to CN201910321095.XA priority Critical patent/CN110001371B/en
Publication of CN110001371A publication Critical patent/CN110001371A/en
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K1/00—Arrangement or mounting of electrical propulsion units
    • B60K1/02—Arrangement or mounting of electrical propulsion units comprising more than one electric motor
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/06—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing
    • B60K17/08—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing of mechanical type
    • 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0806—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with a plurality of driving or driven shafts
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2051—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with eight engaging means

Abstract

The invention discloses an opposite type double-motor power coupling automatic transmission, which allows driving motors to be oppositely arranged, can maximally improve the installation space of matched motors, and is suitable for various double-motor driven new energy automobiles. The special planetary gear mechanism can realize double-motor multi-mode driving, comprises power output of 3 gears of a single motor or power coupling output of 3 gears of the double motor, is provided with a power output function of 2 gears of a standby motor, is used for various new energy automobiles driven by the motor, such as large cars, off-road vehicles, trucks or commercial vehicles, and the like, can be suitable for different working condition demands of the new energy automobiles, and improves motor driving efficiency, whole vehicle power performance and economy.

Description

Opposite type double-motor power coupling automatic transmission
Technical Field
The invention relates to a transmission, in particular to an opposite double-motor power coupling automatic transmission.
Background
With the development of society, automobiles have entered into thousands of households and become an indispensable transportation means for people to travel. Because the traditional internal combustion engine automobile continuously causes environmental pollution and the petroleum storage is increasingly scarce, the development of new energy automobiles has become an important direction of automobile development. At present, city development is rapid, most of vehicles are used in cities, and the conditions of automobiles in urban operation are stop-and-go and low speed, so that various working conditions exist.
The pure electric vehicle has the advantages of zero emission, no pollution, low noise, high energy utilization rate, convenient maintenance and the like, is taken as an alternative scheme of the traditional vehicle by a plurality of factories, and most of driving motors of the pure electric vehicle are matched by adopting peak power, and under certain urban working conditions, the motors are not required to output larger power, so that the waste of output power is caused, the power consumption is increased, and the cruising mileage is reduced. For this reason, many manufacturers have proposed a dual-motor-coupled automatic transmission using multi-mode driving for solving the above problems, but the dual-motor-coupled automatic transmission currently on the market has the following problems: the automatic transmission has the advantages that certain automatic transmissions are installed on the same side by adopting double motors, so that the outer diameter of the transmission is increased, the installation size and the installation position of a driving motor are limited, and the matching power of the driving motor and the selection of the size of the driving motor are affected; some automatic transmissions also adopt double-motor symmetrical arrangement, but only adopt a mode of matching a single-row planetary gear structure with other plane gear set mechanisms, and the automatic transmission has the advantages of simple structure, large volume and heavy mass; according to the method, the automatic transmission has a power coupling function, but can not realize the switching between independent driving and coupling driving of the double motors, and the coupling driving mode is single.
Disclosure of Invention
In order to solve the defects in the prior art, the invention aims to provide an opposite type double-motor power coupling automatic transmission.
In order to achieve the above purpose, the present invention adopts the following technical scheme:
an opposite type double-motor power coupling automatic transmission comprises a transmission shell, a first planetary gear mechanism, a second planetary gear mechanism, a driving motor A, a driving motor B, a power coupling gear mechanism and a main speed reducer mechanism, wherein the first planetary gear mechanism and the second planetary gear mechanism are arranged on two sides of the transmission shell;
the first planetary gear mechanism comprises a sun gear A arranged on a first input shaft, a planet carrier A is sleeved in a shaft space where the sun gear A is positioned, a clutch C1 is arranged on one side of the planet carrier A and fixedly connected with an outer ring of the planet carrier A, a plurality of planet gears A are arranged on the planet carrier A, the inner sides of the planet gears A are meshed with the sun gear A, the outer sides of the planet gears A are meshed with an outer ring gear A, a brake B1 is arranged on the outer side of the outer ring gear A and fixedly connected with an inner ring of the outer ring gear A, and an outer ring of the brake B1 is fixedly arranged on a transmission shell;
the second planetary gear mechanism comprises a sun gear B arranged on a second input shaft, a planet carrier B is sleeved in a shaft space where the sun gear B is positioned, a clutch C3 is arranged on one side of the planet carrier B and fixedly connected with an outer ring of the planet carrier B, a plurality of planet gears B are arranged on the planet carrier B, the inner sides of the planet gears B are meshed with the sun gear B, the outer sides of the planet gears B are meshed with an outer ring gear B, a brake B2 is arranged on the outer side of the outer ring gear B and fixedly connected with an inner ring of the outer ring gear B, and an outer ring of the brake B2 is fixedly arranged on a transmission shell;
the power coupling gear mechanism comprises a bevel gear set which is respectively connected with the first planetary gear mechanism and the second planetary gear mechanism and used for coupling the power of the driving motor A and the driving motor B, and a bevel gear set which is used for power linkage of the first planetary gear mechanism and the second planetary gear mechanism.
Further, the driving motor A and the driving motor B are symmetrically arranged on two sides of the transmission shell.
Further, an output shaft of the driving motor A can be connected with a first input shaft through a motor clutch A.
Further, an output shaft of the driving motor B can be connected with a second input shaft through a motor clutch B.
Further, the main speed reducer mechanism structure comprises a built-in main speed reducer and a differential mechanism, the built-in main speed reducer comprises a bevel pinion and a bevel gear, the bevel pinion is connected with a bevel gear D, the bevel gear is connected with a differential mechanism shell, the differential mechanism is arranged in the differential mechanism shell, and the bevel gears on two sides of the differential mechanism respectively transmit power to an output shaft A and an output shaft B.
Further, the bevel gear group comprises a bevel gear A, a bevel gear B, a bevel gear C and a bevel gear D, wherein the bevel gear A is fixedly connected with one side, close to the center of the transmission, of the planet carrier A, a large bevel gear is fixedly connected with one side, close to the center of the transmission, of the planet carrier B, a clutch C4 is arranged on one side, close to the center of the transmission, of the large bevel gear, and is fixedly connected with the outer ring of the large bevel gear, the bevel gear B is sleeved on one side, close to the center, of an input shaft where the sun gear B is located, a clutch C4 is arranged on one side, close to the planet carrier B, of the bevel gear B, is fixedly connected with the inner ring of the large bevel gear, and the bevel gear C and the bevel gear D are respectively horizontally meshed with the bevel gear A and the bevel gear B at 90 degrees.
Furthermore, the planet carrier B is fixedly connected with the outer side of the large bevel gear in a meshed manner, the bevel gear C is meshed with the bevel gear B, a clutch C2 is arranged on one side, close to the center of the transmission, of the shaft where the bevel gear B is positioned and fixedly connected with the outer ring of the bevel gear B, a bevel gear A is arranged at a symmetrical position of the bevel gear B, a clutch C2 is arranged on one side, close to the center of the transmission, of the shaft where the bevel gear A is positioned and fixedly connected with the inner ring of the bevel gear A, the bevel gear A is fixedly connected with the large bevel gear in a meshed manner, and the large bevel gear of the outer ring gear A is fixedly connected with one side, close to the center of the transmission, of the outer ring gear A.
The invention adopts the technical proposal, and has the following advantages: the transmission mechanism with the combination of the opposite double-row planetary gear mechanism, the bevel gear set and the plane gear set is adopted, so that the torque distribution of the transmission is more reasonable, the size of the gear set can be greatly reduced, and the transmission is more compact in structure, smaller in size and lighter in weight; the adoption of the small-size opposite power coupling mechanism can reduce the limit of a general coupling transmission on the installation position of the driving motor, so that the transmission is matched with driving motors with various power under the condition of allowing the size, and the motor is convenient to install and maintain; the opposite double-row planetary gear mechanism is adopted and matched with the bevel gear set and other gear mechanisms to realize power coupling, so that the coupling power is more stable, the transmission efficiency is high, and the motor speed regulation is simpler and faster; the four-wheel motor adopts a double-motor multi-mode control mode, so that the power output of 3 gears of a single motor or the power coupling output of 3 gears of the double motor can be realized, a standby motor 2-gear power output function is arranged, different working conditions of a vehicle can be adapted, and the power performance, the economy and the cruising ability of a new energy automobile can be improved by multi-mode driving; the opposite double-motor power coupling automatic transmission can realize front-mounted and rear-mounted driving of the driving assembly through the matched main speed reducer differential, and can also omit the differential to realize front-mounted rear-mounted or middle-mounted rear-mounted driving of the driving assembly.
Drawings
The invention is described in further detail below with reference to the attached drawings and detailed description:
FIG. 1 is a schematic diagram of an overall structure of an opposed dual-motor power coupling automatic transmission according to the present invention;
FIG. 2 is a schematic diagram of a first gear drive power transmission of an automatic transmission drive motor A according to the present invention;
FIG. 3 is a schematic diagram of a second gear drive power transmission for an automatic transmission drive motor A according to the present invention;
FIG. 4 is a schematic diagram of a direct drive power transmission for an automatic transmission drive motor A according to the present invention;
FIG. 5 is a schematic illustration of an automatic transmission dual motor coupling first gear drive power transmission according to the present invention;
FIG. 6 is a schematic diagram of an automatic transmission dual motor coupled two speed drive power transmission according to the present invention;
FIG. 7 is a schematic illustration of a dual motor coupled direct drive power transmission for an automatic transmission according to the present invention;
FIG. 8 is a schematic diagram of a first gear drive power transmission for an automatic transmission drive motor B according to the present invention;
fig. 9 is a schematic diagram showing a direct-range driving power transmission of an automatic transmission driving motor B according to the present invention.
Fig. 10 is a schematic view of the structure of the present invention (single output shaft).
Reference numerals:
in the figure: 1. the drive motors a,2, motor clutches a,3, transmission housings, 4, clutches C1,5, sun gears a,6, carriers a,7, planetary gears a,8, outer gear rings a,9, brakes B1, 10, bevel gears C,11, outer gear ring a fixed large bevel gear, 12, bevel gears a,13, clutches C2, 14, bevel gears B,15, bevel gears C,16, carrier B fixed large bevel gear, 17, brakes B2, 18, outer gear rings B,19, planetary gears B,20, carrier B,21, sun gears B,22, clutches C3, 23, motor clutches B,24, drive motors B,25, bevel gears B,26, clutches C4, 27, bevel gears D,28, output shafts B,29, built-in final drives, 30, differential housings, 31, differentials, 32, output shafts a,33, bevel gears a.
Detailed Description
The invention designs an opposite type double-motor power coupling automatic transmission, which has a completely different structural arrangement mode compared with other similar transmissions, and adopts a mechanism combining a double-row planetary gear set, a bevel gear set and a plane gear set, so that the transmission has more compact structure and more reasonable mechanism arrangement, and has the following characteristics: the transmission mechanism with the combination of the opposite double-row planetary gear mechanism, the bevel gear set and the plane gear set is adopted, so that the torque distribution of the transmission is more reasonable, the size of the gear set can be greatly reduced, and the transmission is more compact in structure, smaller in size and lighter in weight; the adoption of the small-size opposite power coupling mechanism can reduce the limit of a general coupling transmission on the installation position of the driving motor, so that the transmission is matched with driving motors with various power under the condition of allowing the size, and the motor is convenient to install and maintain; the opposite double-row planetary gear mechanism is adopted and matched with the bevel gear set and other gear mechanisms to realize power coupling, so that the coupling power is more stable, the transmission efficiency is high, and the motor speed regulation is simpler and faster; the four-wheel motor adopts a double-motor multi-mode control mode, so that the power output of 3 gears of a single motor or the power coupling output of 3 gears of the double motor can be realized, a standby motor 2-gear power output function is arranged, different working conditions of a vehicle can be adapted, and the power performance, the economy and the cruising ability of a new energy automobile can be improved by multi-mode driving; the opposite double-motor power coupling automatic transmission can realize front-mounted and rear-mounted driving of the driving assembly through the matched main speed reducer differential, and can also omit the differential to realize front-mounted rear-mounted or middle-mounted rear-mounted driving of the driving assembly.
In order to enable those skilled in the art to better understand the technical scheme of the present invention, the following detailed description of the embodiments of the present invention is provided with reference to the accompanying drawings.
As shown in fig. 1, the opposed two-motor power-coupling automatic transmission is divided into 4 parts: 2 side planetary gear mechanism, central power coupling gear mechanism and main reducer (including differential) mechanism, respectively described below:
as shown in fig. 1, the drive motor a (1) and the drive motor B (24) are symmetrically arranged on both sides of a transmission case (3) of the opposed two-motor power-coupling automatic transmission. The planetary gear mechanism on one side of the driving motor A (1) has the following structure: an output shaft of the driving motor A (1) can be connected with an input shaft of a sun gear A (5) through a motor clutch A (2), a clutch C1 (4) is arranged at the input shaft end of the sun gear A (5) and fixedly connected with an inner ring of the sun gear A, a planet carrier A (6) is sleeved in a shaft space where the sun gear A (5) is positioned, and a clutch C1 (4) is arranged at one side of the planet carrier A (6) and fixedly connected with an outer ring of the planet carrier A; a plurality of planet gears A (7) are arranged on the planet carrier A (6), the inner sides of the planet gears A (7) are meshed with the sun gear A (5), and the outer sides of the planet gears A (7) are meshed with the outer gear ring A (8) to form a planet gear mechanism; the outer side of the outer gear ring A (8) is provided with a brake B1 (9) and fixedly connected with the inner ring of the outer gear ring A, and the outer ring of the brake B1 (9) is fixedly arranged on the transmission shell (3). The motor clutch A (2) is used for timely connecting or disconnecting the power of the driving motor A (1) during gear shifting so as to match with the gear shifting of a transmission; the clutch C1 (4) is used for connecting the sun gear A (5) with the planet carrier A (6) and rotating together; the function of the brake B1 (9) is to release or lock the outer ring gear a (8).
As shown in fig. 1, the planetary gear mechanism on the side of the drive motor B (24) is structured as follows: an output shaft of a driving motor B (24) can be connected with an input shaft of a sun gear B (21) through a motor clutch B (23), a clutch C3 (22) is arranged at the input shaft end of the sun gear B (21) and fixedly connected with the inner ring of the sun gear B, a planet carrier B (20) is sleeved in a shaft space where the sun gear B (21) is positioned, and a clutch C3 (22) is arranged at one side of the planet carrier B (20) and fixedly connected with the outer ring of the planet carrier B; a plurality of planet gears B (19) are arranged on the planet carrier B (20), the inner sides of the planet gears B (19) are meshed with the sun gear B (21), and the outer sides of the planet gears B (19) are meshed with the outer gear ring B (18) to form a planet gear mechanism; the brake B2 (17) is arranged on the outer side of the outer gear ring B (18) and fixedly connected with the inner ring of the outer gear ring B, and the outer ring of the brake B2 (17) is fixedly arranged on the transmission shell (3). The motor clutch B (23) is used for connecting or disconnecting the power of the driving motor B (24) at the right time during gear shifting so as to match with the gear shifting of a transmission; the clutch C3 (22) is used for connecting the sun gear B (21) and the planet carrier B (20) and rotating together; the function of the brake B2 (17) is to release or lock the external ring gear B (18).
As shown in fig. 1, the structure of the central power coupling gear mechanism is as follows: a bevel gear A (33) is fixedly connected to one side of the planet carrier A (6) close to the center of the transmission; a planet carrier B (20) is installed on one side, close to the center of the transmission, of a planet carrier B fixedly connected with a large bevel gear (16), a clutch C4 (26) is installed on one side, close to the center of the transmission, of the planet carrier B fixedly connected with the large bevel gear (16) and fixedly connected with the outer ring of the large bevel gear, a bevel gear B (25) is sleeved on one side, close to the center, of an input shaft where a sun gear B (21) is located, of the bevel gear B, and a clutch C4 (26) is installed on one side, close to the planet carrier B, fixedly connected with the large bevel gear (16) and fixedly connected with the inner ring of the bevel gear; bevel gears C (10) and D (27) which are horizontally meshed with the bevel gears A (33) and B (25) at 90 degrees form a bevel gear group with two-side motors in power coupling; the planet carrier B is fixedly connected with a big bevel gear (16) and is meshed with a bevel gear C (15), the bevel gear C (15) is meshed with a bevel gear B (14), a clutch C2 (13) is arranged on one side, close to the center of the transmission, of a shaft where the bevel gear B (14) is located and is fixedly connected with the outer ring of the bevel gear B, a bevel gear A (12) is arranged at a symmetrical position of the bevel gear B (14), a clutch C2 (13) is arranged on one side, close to the center of the transmission, of the shaft where the bevel gear A (12) is located and is fixedly connected with the inner ring of the bevel gear A, the bevel gear A (12) is fixedly connected with a big bevel gear (11) and is meshed with the big bevel gear A, the big bevel gear A (11) is arranged on one side, close to the center of the transmission, of the bevel gear A (8) is used for realizing power linkage of planetary gear sets on two sides. The clutch C4 (26) is used for connecting or disconnecting the power transmission between the planet carrier B fixedly connected large bevel gear (16) and the bevel gear B (25), and the clutch C2 (13) is used for connecting or disconnecting the power transmission between the shaft of the bevel gear B (14) and the shaft of the bevel gear A (12).
As shown in fig. 1, the final drive (including differential) mechanism is structured as follows: one side of the bevel gear D (27) far away from the center of the transmission is connected with a built-in main speed reducer (29) through a small bevel gear, a large bevel gear of the built-in main speed reducer (29) is connected with a differential case (30), a differential mechanism (31) is arranged in the differential case (30), and bevel gears at two sides in the differential mechanism (31) respectively transmit power to an output shaft A (32) and an output shaft B (28). The main speed reducer (including differential) mechanism is similar to the existing and mature automobile main speed reducer (differential) structure.
The transmission shafts of the gear sets are all arranged on a transmission shell (3) through corresponding bearings, and each clutch and each brake adopt a current mature multi-disc type hydraulic control structure, which is not shown in the figure.
Further, the following sub-working conditions describe the working principles of each gear of the opposite type double-motor power coupling automatic transmission:
as shown in fig. 2, in the first-gear driving power transmission path of the driving motor a of the automatic transmission, when the automobile is in a low-load state, the automobile is driven by the driving motor a (1) only through the main motor, and at the moment, the motor clutch a (2) works to transmit the power of the driving motor a (1) to the input shaft where the sun gear a (5) is located, and meanwhile, the brake B1 (9) works to lock the external gear ring a (8). At this time, the power output route: the driving motor A (1), the motor clutch A (2), the sun gear A (5), the planetary gear A (7), the planet carrier A (6), the bevel gear A (33), the bevel gear D (27), the built-in main speed reducer (29), the differential case (30), the differential (31), the output shaft B (28) and the output shaft A (32). At this time, each of the other gear sets is in an idle state, and each of the other brakes, clutches, drive motor B (24), and motor clutch B (23) are not operated.
As shown in fig. 3, in this automatic transmission driving motor a second gear driving power transmission line, when the automobile is in a low load state, the automobile is not required to be driven and accelerated by a double motor, and the automobile is driven to run only by a main motor, namely the driving motor a (1), at this time, the motor clutch a (2) works, so that the driving motor a (1) power is transmitted to the input shaft where the sun gear a (5) is located, and meanwhile: the clutch C2 (13) works to combine the power of the shaft where the bevel gear A (12) is positioned with the shaft where the bevel gear B is positioned, the clutch C4 (26) works to fixedly connect the bevel gear B (25) with the planet carrier B and combine the power of the bevel gear (16). At this time, the power output route: the power is partly from the drive motor A (1), the motor clutch A (2), the sun gear A (5), the planetary gear A (7), the planetary carrier A (6), the bevel gear A (33), the bevel gear D (27) through the bevel gear C (10), the bevel gear B (25), the planetary carrier B fixedly connected with the big bevel gear (16), the bevel gear C (15), the bevel gear B (14), the clutch C2 (13), the bevel gear A (12), the outer gear A fixedly connected with the big bevel gear (11), the outer gear A (8) is driven to rotate at a slow speed (in the same direction as the sun gear and the planetary carrier), the transmission ratio of the power through the gear mechanism is reduced (so that the first gear speed is faster), the speed of the output speed of the transmission is realized, and the two power flows into the differential case (30), the differential case (31) and the output shaft B (32) through the bevel gear D (27). At this time, each of the other gear sets is in an idle state, and each of the other brakes, clutches, drive motor B (24), and motor clutch B (23) are not operated.
As shown in fig. 4, in the direct gear driving power transmission route of the automatic transmission driving motor a, when the automobile is in a low load state, the automobile is not required to be driven and accelerated by adopting double motors, the automobile is driven to run only by the main motor, namely the driving motor a (1), at the moment, the motor clutch a (2) works, the power of the driving motor a (1) is transmitted to the input shaft where the sun gear a (5) is located, meanwhile, the clutch C1 (4) works, and the input shaft where the sun gear a (5) is located is fixedly connected with the planet carrier a (6), so that the power is directly transmitted. At this time, the power output route: the power is from the driving motor A (1), the motor clutch A (2), the sun gear A (5), the planet carrier A (6), the bevel gear A (33), the bevel gear D (27), the built-in main speed reducer (29), the differential mechanism shell (30), the differential mechanism (31), the output shaft B (28) and the output shaft A (32). At this time, each of the other gear sets is in an idle state, and each of the other brakes, clutches, drive motor B (24), and motor clutch B (23) are not operated.
As shown in fig. 5, in the first gear coupling driving power transmission route of the driving motor a and the driving motor B of the automatic transmission, when the automobile is in a medium and heavy load state, the automobile is started by adopting double motor driving, and the automobile jointly drives the automobile to start and run through the main motor, the auxiliary motor, namely the driving motor a (1) and the driving motor B (24), at the moment: the motor clutch A (2) works to transmit the power of the driving motor A (1) to an input shaft where the sun gear A (5) is positioned, and the brake B1 (9) works to lock the outer gear ring A (8); the motor clutch B (23) works, the driving motor B (24) transmits the power of the driving motor B (24) to the input shaft where the sun gear B (21) is positioned, and the brake B2 (17) works to lock the outer gear ring B (18); the clutch C4 (26) works to fixedly connect the bevel gear B (25) with the planet carrier B and combine the power with the big bevel gear (16). At this time, the power output route: the power of the driving motor A (1) is from the driving motor A (1), the motor clutch A (2), the sun gear A (5), the planetary gear A (7), the planetary carrier A (6), the bevel gear A (33) and the bevel gear D (27); the power of the driving motor B (24) is from the driving motor B (24), the clutch B (23), the sun gear B (21), the planetary gear B (19), the planetary carrier B (20), the fixedly connected large bevel gear (16) of the planetary carrier B, the bevel gear B (25) and the bevel gear D (27); the input power of the two motors is coupled at a bevel gear D (27) and transmitted to a built-in final drive (29), a differential case (30), a differential (31), an output shaft B (28) and an output shaft A (32). At this time, the input shaft steering of the driving motor A (1) and the driving motor B (24) should be opposite, that is, the driving motor B (24) should be rotated anticlockwise when the driving motor A (1) rotates clockwise, so that the rotation speed and the torque can be smoothly coupled at the bevel gear D (27), and other gear sets are in idle state, and other brakes and clutches do not work.
As shown in fig. 6, in the two-gear coupling driving power transmission route of the driving motor a and the driving motor B of the automatic transmission, when the automobile is in a medium and heavy load state, the automobile is driven by two motors, and the automobile drives the automobile to travel together through a main motor, a sub motor, namely the driving motor a (1) and the driving motor B (24), at this time: the motor clutch A (2) works to transmit the power of the driving motor A (1) to an input shaft where the sun gear A (5) is positioned; the motor clutch B (23) works, power of the driving motor B (24) is transmitted to an input shaft where the sun gear B (21) is positioned, the brake B2 (17) works, and the outer gear ring B (18) is locked; the clutch C2 (13) works to combine the shaft of the bevel gear A (12) with the shaft of the bevel gear B (14) to power. At this time, the power output route: the power of the driving motor A (1) is from the driving motor A (1), the motor clutch A (2), the sun gear A (5), the planetary gear A (7) and the planet carrier A (6); the power of the driving motor B (24) is from the driving motor B (24), the clutch B (23), the sun gear B (21), the planetary gear B (19), the planetary carrier B (20), the planetary carrier B fixedly connected with the big bevel gear (16), the bevel gear C (15), the bevel gear B (14), the clutch C2 (13), the bevel gear A (12), the big bevel gear A fixedly connected with the big bevel gear (11), the outer gear A (8) and the planetary carrier A (6), the outer gear A (8) is driven to rotate slowly (rotate in the same direction with the sun gear and the planetary carrier), and the transmission ratio of the power is reduced through the transmission of the gear mechanism, so that the speed of the output of the transmission is faster than that of the first gear, and the speed of the output of the transmission is increased; the two power flows are coupled at the planet carrier A (6) and are transmitted from the bevel gear A (33) to the bevel gear D (27), the built-in main speed reducer (29), the differential case (30), the differential (31), the output shaft B (28) and the output shaft A (32). At this time, the input shaft steering of the driving motor A (1) and the driving motor B (24) should be opposite, that is, the driving motor B (24) should be rotated anticlockwise when the driving motor A (1) rotates clockwise, so that the power is transmitted to the position of the planet carrier A (6) to smoothly couple the rotating speed and the torque, and other gear sets are in idle states, and other brakes and clutches do not work.
As shown in fig. 7, in the present automatic transmission driving motor a and driving motor B direct gear coupling driving power transmission line, when the vehicle is in a medium and heavy load state, it is necessary to use dual motor driving, and the vehicle drives the vehicle together by the main motor, the auxiliary motor, that is, the driving motor a (1) and the driving motor B (24), at this time: the motor clutch A (2) works to transmit the power of the driving motor A (1) to the input shaft where the sun gear A (5) is positioned, meanwhile, the clutch C1 (4) works to fixedly connect the input shaft where the sun gear A (5) is positioned with the planet carrier A (6) and directly transmit the power; the motor clutch B (23) works to transmit the power of the driving motor B (24) to the input shaft where the sun gear B (21) is located, meanwhile, the clutch C3 (22) and the clutch C4 (26) work to fixedly connect the input shaft where the sun gear B (21) is located with the planet carrier B (20), and the planet carrier B is fixedly connected with the big bevel gear (16) and the bevel gear B (25) to directly transmit the power. At this time, the power output route: the power of the driving motor A (1) is from the driving motor A (1), the motor clutch A (2), the sun gear A (5), the planet carrier A (6), the bevel gear A (33) and the bevel gear D (27); the power of the driving motor B (24) is from the driving motor B (24), the motor clutch B (23), the sun gear B (21), the planet carrier B (20), the planet carrier B fixedly connected with the large bevel gear (16), the bevel gear B (25) and the bevel gear D (27); the input power of the two motors is coupled at a bevel gear D (27) and transmitted to a built-in final drive (29), a differential case (30), a differential (31), an output shaft B (28) and an output shaft A (32). At this time, the input shaft steering of the driving motor A (1) and the driving motor B (24) should be opposite, that is, the driving motor B (24) should be rotated anticlockwise when the driving motor A (1) rotates clockwise, so that the rotation speed and the torque can be smoothly coupled at the bevel gear D (27), and other gear sets are in idle state, and other brakes and clutches do not work.
As shown in fig. 8, in the present automatic transmission, when the driving motor a fails or the driving motor a related controller or the transmission fails, the transmission is switched to drive and start by the driving motor B (24) which is a sub-motor, and at this time, the motor clutch B (23) is operated, the driving motor B (24) transmits the driving motor B (24) to the input shaft where the sun gear B (21) is located, and the brake B2 (17) is operated, thereby locking the external ring gear B (18); the clutch C4 (26) works to fixedly connect the bevel gear B (25) with the planet carrier B and combine the power with the big bevel gear (16). At this time, the power output route: the device comprises a driving motor B (24), a clutch B (23), a sun gear B (21), a planetary gear B (19), a planetary carrier B (20), a large bevel gear (16) fixedly connected with the planetary carrier B, a bevel gear B (25), a bevel gear D (27), a built-in main speed reducer (29), a differential mechanism shell (30), a differential mechanism (31), an output shaft B (28) and an output shaft A (32). At this time, the other gear sets are in an idle state, and the other brakes, clutches, drive motor a (1), and motor clutch a (2) are not operated.
As shown in fig. 9, in the present automatic transmission driving motor B direct gear driving power transmission path, when the driving motor a fails or the driving motor a related controller or the transmission fails, the transmission will be switched to drive and run only through the auxiliary motor, that is, the driving motor B (24), at this time, the motor clutch B (23) works, the driving motor B (24) transmits the driving motor B (24) power to the input shaft where the sun gear B (21) is located, meanwhile, the clutch C3 (22) and the clutch C4 (26) work, the input shaft where the sun gear B (21) is located is fixedly connected with the planet carrier B (20), the planet carrier B is fixedly connected with the large bevel gear (16) and the bevel gear B (25), and the power can be directly transmitted. At this time, the power output route: the power is from a driving motor B (24), a motor clutch B (23), a sun gear B (21), a planet carrier B (20), a large bevel gear fixedly connected with the planet carrier B (16), a bevel gear B (25), a bevel gear D (27), a built-in main speed reducer (29), a differential mechanism shell (30), a differential mechanism (31), an output shaft B (28) and an output shaft A (32). At this time, the other gear sets are in an idle state, and the other brakes, clutches, drive motor a (1), and motor clutch a (2) are not operated.
The driving motor B in fig. 8 and 9 is driven separately to operate as a standby mode of the transmission, and the speed regulation range of the driving motor B is increased by the controller to adapt to the rotation speed of the first gear directly shifted into the direct gear, so that the dynamic performance of the driving mode is slightly inferior to that of the conventional driving mode.
In summary, the following table is a working principle table of each driving motor, clutch and brake in different working modes of the opposite type double-motor power coupling automatic transmission:
as shown in fig. 10, the opposite type double-motor power coupling automatic transmission is installed on a front-drive or middle-drive vehicle of a driving assembly, and a main speed reducer and differential mechanism structure can be omitted, and the working principle is the same as that of the transmission comprising the main speed reducer and the differential mechanism, except that the main speed reducer and the differential mechanism structure are replaced by a single output shaft.
The above description is not intended to limit the invention to the particular embodiments disclosed, but on the contrary, the intention is to cover all modifications, equivalents, and alternatives falling within the spirit and principles of the invention.

Claims (2)

1. An automatic transmission of opposite type bi-motor power coupling, which is characterized in that: the transmission comprises a transmission shell, a first planetary gear mechanism, a second planetary gear mechanism, a driving motor A, a driving motor B, a power coupling gear mechanism and a main speed reducer mechanism, wherein the first planetary gear mechanism and the second planetary gear mechanism are arranged on two sides of the transmission shell;
the first planetary gear mechanism comprises a sun gear A arranged on a first input shaft, a planet carrier A is sleeved in a shaft space where the sun gear A is positioned, a clutch C1 is arranged on one side of the planet carrier A and fixedly connected with an outer ring of the planet carrier A, a plurality of planet gears A are arranged on the planet carrier A, the inner sides of the planet gears A are meshed with the sun gear A, the outer sides of the planet gears A are meshed with an outer ring gear A, a brake B1 is arranged on the outer side of the outer ring gear A and fixedly connected with an inner ring of the outer ring gear A, and an outer ring of the brake B1 is fixedly arranged on a transmission shell;
the second planetary gear mechanism comprises a sun gear B arranged on a second input shaft, a planet carrier B is sleeved in a shaft space where the sun gear B is positioned, a clutch C3 is arranged on one side of the planet carrier B and fixedly connected with an outer ring of the planet carrier B, a plurality of planet gears B are arranged on the planet carrier B, the inner sides of the planet gears B are meshed with the sun gear B, the outer sides of the planet gears B are meshed with an outer ring gear B, a brake B2 is arranged on the outer side of the outer ring gear B and fixedly connected with an inner ring of the outer ring gear B, and an outer ring of the brake B2 is fixedly arranged on a transmission shell;
the power coupling gear mechanism comprises a bevel gear set, a bevel gear set and a gear assembly, wherein the bevel gear set is respectively connected with the first planetary gear mechanism and the second planetary gear mechanism and used for coupling the power of the driving motor A and the driving motor B;
an output shaft of the driving motor A can be connected with a first input shaft through a motor clutch A;
an output shaft of the driving motor B can be connected with a second input shaft through a motor clutch B;
the main speed reducer mechanism structure comprises a built-in main speed reducer and a differential mechanism, wherein the built-in main speed reducer comprises a small bevel gear and a large bevel gear, the small bevel gear is connected with the bevel gear D, the large bevel gear is connected with a differential mechanism shell, the differential mechanism is arranged in the differential mechanism shell, and the bevel gears on two sides of the differential mechanism respectively transmit power to an output shaft A and an output shaft B;
the bevel gear group comprises a bevel gear A, a bevel gear B, a bevel gear C and a bevel gear D, wherein the bevel gear A is fixedly connected with one side, close to the center of the transmission, of a planet carrier A;
the planetary carrier B is fixedly connected with the outer side of the large bevel gear in a meshed manner, the bevel gear C is meshed with the bevel gear B, a clutch C2 is arranged on one side, close to the center of the transmission, of the shaft where the bevel gear B is located and fixedly connected with the outer ring of the bevel gear B, a bevel gear A is arranged at a symmetrical position with the bevel gear B, a clutch C2 is arranged on one side, close to the center of the transmission, of the shaft where the bevel gear A is located and fixedly connected with the inner ring of the bevel gear A, the bevel gear A is fixedly connected with the large bevel gear in a meshed manner, and the large bevel gear of the outer ring gear A is fixedly connected with one side, close to the center of the transmission, of the outer ring gear A.
2. An opposed dual-motor power-coupling automatic transmission as defined in claim 1, wherein: the driving motor A and the driving motor B are symmetrically arranged on two sides of the transmission shell.
CN201910321095.XA 2019-04-19 2019-04-19 Opposite type double-motor power coupling automatic transmission Active CN110001371B (en)

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CN110752705B (en) * 2019-10-15 2020-08-11 中国矿业大学(北京) Intelligent semi-direct-drive type scraper conveyor with parallel permanent magnet motors

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102198790A (en) * 2011-05-03 2011-09-28 重庆大学 Hybrid power vehicle transmission system of two-stage planetary gear mechanism
CN204547733U (en) * 2015-03-07 2015-08-12 合肥工业大学 Two gear variable speed drive systems of the plug-in hybrid-power automobile of single drive motor
CN106004408A (en) * 2016-06-28 2016-10-12 重庆大学 Double-planetary-mechanism hybrid power automobile transmission system
DE102016101063A1 (en) * 2016-01-21 2017-07-27 Volkswagen Aktiengesellschaft Gear arrangement for a motor vehicle and motor vehicle
CN209852061U (en) * 2019-04-19 2019-12-27 福建工程学院 Opposed double-motor power coupling automatic transmission

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102198790A (en) * 2011-05-03 2011-09-28 重庆大学 Hybrid power vehicle transmission system of two-stage planetary gear mechanism
CN204547733U (en) * 2015-03-07 2015-08-12 合肥工业大学 Two gear variable speed drive systems of the plug-in hybrid-power automobile of single drive motor
DE102016101063A1 (en) * 2016-01-21 2017-07-27 Volkswagen Aktiengesellschaft Gear arrangement for a motor vehicle and motor vehicle
CN106004408A (en) * 2016-06-28 2016-10-12 重庆大学 Double-planetary-mechanism hybrid power automobile transmission system
CN209852061U (en) * 2019-04-19 2019-12-27 福建工程学院 Opposed double-motor power coupling automatic transmission

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