CN104565264B - Two-gear automatic transmission for pure electric vehicles - Google Patents
Two-gear automatic transmission for pure electric vehicles Download PDFInfo
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- CN104565264B CN104565264B CN201410836083.8A CN201410836083A CN104565264B CN 104565264 B CN104565264 B CN 104565264B CN 201410836083 A CN201410836083 A CN 201410836083A CN 104565264 B CN104565264 B CN 104565264B
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- 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
-
- 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
- F16H37/0813—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 with only one input shaft
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- 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
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/089—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears all of the meshing gears being supported by a pair of parallel shafts, one being the input shaft and the other the output shaft, there being no countershaft involved
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- 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
- B60K2001/001—Arrangement or mounting of electrical propulsion units one motor mounted on a propulsion axle for rotating right and left wheels of this axle
-
- 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
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H2003/0818—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts comprising means for power-shifting
-
- 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
- F16H2200/0021—Transmissions for multiple ratios specially adapted for electric vehicles
-
- 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
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0034—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising two forward speeds
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Structure Of Transmissions (AREA)
- Transmission Devices (AREA)
Abstract
Disclosed is a two-gear automatic transmission for pure electric vehicles. The two-gear automatic transmission is characterized by comprising an input shaft, a first intermediate shaft, a second intermediate shaft, a first cylindrical gear pair, a second cylindrical gear pair, a third cylindrical gear pair, a first torque transmission device, a second torque transmission device and a differential assembly; rotary center lines of the input shaft, the second intermediate shaft and the differential assembly are parallel to one another. The two-gear automatic transmission solves the problem that the existing two-gear automatic transmission for pure electric vehicles has high requirements on a driving motor and a battery, the driving motor is low in operational efficiency and the like, and power performance and economical efficiency of the pure electric vehicles are improved.
Description
Technical field
The present invention relates to a kind of two shift transmissions, particularly relate to a kind of two-shift automatic speed variator being applied to pure electric automobile, belong to
In automobile technical field.
Background technology
Power transmission technology belongs to the core technology of pure electric automobile, and its type and performance directly determine the power of pure electric automobile
Performance and energy consumption level.In the case of driving motor performance certain, in order to improve the torque of driving wheel further, reach pure electricity
The dynamic property requirement of electrical automobile, and the relation between motor speed and speed can be regulated, often use variable speed drive.Mesh
Before, pure electric automobile uses single gear decelerator, and its simple in construction, volume are little, light weight, low cost, in running
Without gearshift, there is not the situation of power interruption.
But, when using single gear decelerator, higher to driving motor to require, it is desirable to drive motor can provide relatively in permanent torque district
High driving torque, can provide again higher rotating speed, to meet the requirement that vehicle accelerates, climbs and runs at high speed in invariable power district.
Meanwhile, single gear decelerator is used to be unfavorable for improving the efficiency of electric drive assembly system.This is because single transmission cannot be same than generally
Time take into account dynamic property and the economy of pure electric automobile, driving process drives motor most cases cannot be in efficiency operation point,
Especially under the highest or minimum speed and low load condition, drive electric efficiency typically can be down to below 60-70%, seriously wave
Take vehicle-mounted electric energy and reduce continual mileage.It addition, single gear decelerator is also unfavorable for using high efficiency, light-weighted driving motor.
In order to make pure electric automobile can preferably play its superiority, reduce driving motor and the requirement of battery, pure electric automobile simultaneously
Power drive system should use multi-shifting speed variator, by the manipulation of multi-shifting speed variator ensureing, driving motor can be operated in more
Ideal high efficiency region, thus improve the indexs such as the dynamic property of car load, economy.
Compared to more gears even continuous variable transmission, two shift transmissions are the compactest due to structure, and power density is higher,
Can realize power shifting, technology relative maturity, require lower to motor, power drive system integrated cost is lower, can guarantee that simultaneously
Higher transmission efficiency, higher in the probability of pure electric automobile field popularization and application on a large scale, can faster industrialization and the marketization,
Thus there is bigger feasibility.
Summary of the invention
(1) purpose
It is an object of the invention to provide a kind of pure electric automobile two-shift automatic speed variator, to solve existing pure electric automobile use
Single gear decelerator, to driving motor and the problem such as battery request is higher, drive motor operational efficiency relatively low, improves pure electric automobile
Dynamic property and economy.
(2) technical scheme
One pure electric automobile two-shift automatic speed variator of the present invention, comprise power shaft, the first jackshaft, the second jackshaft,
One cylindrical gear pair, the second cylindrical gear pair, the 3rd cylindrical gear pair, the first torque transmitter, the second torque transmitter,
And differential assembly.Wherein:
1) described power shaft cross section is circular；
2) described first jackshaft cross section is circular；
3) described second jackshaft cross section is circular；
4) described first cylindrical gear pair can be that straight spur gear is secondary or helical gears are secondary, including the first cylindrical gear pair
Driving gear and the first cylindrical gear pair driven gear；
5) described second cylindrical gear pair can be that straight spur gear is secondary or helical gears are secondary, including the second cylindrical gear pair
Driving gear and the second cylindrical gear pair driven gear；
6) described 3rd cylindrical gear pair can be that straight spur gear is secondary or helical gears are secondary, including the 3rd cylindrical gear pair
Driving gear and the 3rd cylindrical gear pair driven gear；
7) described first torque transmitter can be clutch, lock unit, clutch collar etc., including the first torque transmitter master
Moved end and the first torque transmitter driven end, wherein, described first torque transmitter drive end and the first torque
Transfer device driven end can be selectively engaged, and power shaft and the first cylindrical gear pair driving gear is temporarily connected
Pick up；
8) described second torque transmitter can be clutch, lock unit, clutch collar etc., including the second torque transmitter master
Moved end and the second torque transmitter driven end, wherein, described second torque transmitter drive end and the second torque
Transfer device driven end can be selectively engaged, and the first jackshaft and the second jackshaft is temporarily coupled together；
9) described differential assembly can be selected for the off-the-shelf on market.
Therefore, gear structure and the torque transmitter structure of the present invention can have multiple change because of the change of concrete design requirement
Technical scheme, other gear structure schemes obtained based on the present invention or torque transmitter organization plan are all the present invention's
In claims.
Mutual relation prioritization scheme between them is:
1) rotation centerline of described power shaft, the second jackshaft and differential assembly is parallel to each other；
2) described power shaft, the first torque transmitter, the first cylindrical gear pair driving gear and the second cylindrical gear pair driving tooth
The rotation centerline of wheel overlaps；
3) described first jackshaft, the second jackshaft, the second torque transmitter, the first cylindrical gear pair driven gear, second
The rotation centerline of cylindrical gear pair driven gear and the 3rd cylindrical gear pair driving gear overlaps；
4) rotation centerline of described differential assembly and the 3rd cylindrical gear pair driven gear overlaps；
5) described power shaft and the fixing connection of the first torque transmitter drive end；
6) described power shaft and the fixing connection of the second cylindrical gear pair driving gear；
7) described first jackshaft and the fixing connection of the second cylindrical gear pair driven gear；
8) described first jackshaft and the fixing connection of the second torque transmitter drive end；
9) described second jackshaft and the fixing connection of the second torque transmitter driven end；
10) described second jackshaft and the fixing connection of the first cylindrical gear pair driven gear；
11) described second jackshaft and the fixing connection of the 3rd cylindrical gear pair driving gear；
12) shell and the 3rd cylindrical gear pair driven gear of described differential assembly is fixed and is connected；
13) described first cylindrical gear pair driving gear and the fixing connection of the first torque transmitter driven end；
14) described first cylindrical gear pair driving gear empty set is on power shaft；
15) described first torque transmitter, the first cylindrical gear pair driving gear, the second cylindrical gear pair driving gear are in input
It is arranged in order to away from input near input on the rotation centerline of axle, described 3rd cylindrical gear pair master
Moving gear, the first cylindrical gear pair driven gear, the second torque transmitter, the second cylindrical gear pair driven gear
The rotation centerline of the second jackshaft is arranged in order to away from input near input；
Can also be: described first cylindrical gear pair driving gear, the first torque transmitter, the second cylindrical gear pair master
Moving gear is arranged in order to away from input near input on the rotation centerline of power shaft, and the described 3rd
Cylindrical gear pair driving gear, the first cylindrical gear pair driven gear, the second torque transmitter, the second Cylinder Gear
Wheel set driven gear is arranged to away from input ground successively near input on the rotation centerline of the second jackshaft
Row；
Can also be: described first torque transmitter, the first cylindrical gear pair driving gear, the second cylindrical gear pair master
Moving gear is arranged in order to away from input near input on the rotation centerline of power shaft, and described first
Cylindrical gear pair driven gear, the 3rd cylindrical gear pair driving gear, the second torque transmitter, the second Cylinder Gear
Wheel set driven gear is arranged to away from input ground successively near input on the rotation centerline of the second jackshaft
Row；
Can also be: described first cylindrical gear pair driving gear, the first torque transmitter, the second cylindrical gear pair master
Moving gear is arranged in order to away from input near input on the rotation centerline of power shaft, and described first
Cylindrical gear pair driven gear, the 3rd cylindrical gear pair driving gear, the second torque transmitter, the second Cylinder Gear
Wheel set driven gear is arranged to away from input ground successively near input on the rotation centerline of the second jackshaft
Row.
Their design parameter is:
1) described power shaft diameter is not more than 200 millimeters；
2) described first jackshaft diameter is not more than 200 millimeters；
3) described second jackshaft diameter is not more than 200 millimeters；
4) described first cylindrical gear pair, the second cylindrical gear pair and the 3rd cylindrical gear pair normal module are not more than 10.00 millimeters；
5) described first cylindrical gear pair driving gear, the second cylindrical gear pair driving gear and the 3rd cylindrical gear pair driving gear
The number of teeth is not more than 100；
6) described first cylindrical gear pair driven gear, the second cylindrical gear pair driven gear and the 3rd cylindrical gear pair driven gear
The number of teeth is not more than 200；
7) described first torque transmitter and the second torque transmitter torque capacity are not more than 2000 Newton meters.
The transmission scheme related in the present invention by control described first torque transmitter and the joint of the second torque transmitter or
Separate, produce a gear and two two gears of gear.The brief introduction of work principle of the present invention is as follows:
1) when described first torque transmitter and the second torque transmitter are all in released state, this pure electric automobile is with two
The degree of freedom of speed automatic transmission is 2, and power cannot be transferred to differential assembly from power shaft；
2) when described first torque transmitter be in engagement state, the second torque transmitter be in released state time, this pure electricity
The degree of freedom of electrical automobile two-shift automatic speed variator is 1, is in a gear, and power fills through the first torque transmission from power shaft
Put, the first cylindrical gear pair, the second jackshaft and the 3rd cylindrical gear pair are transferred to differential assembly, power shaft with
The gear ratio that ratio is a gear of the 3rd cylindrical gear pair driven gear rotating speed；
3) when described second torque transmitter be in engagement state, the first torque transmitter be in released state time, this pure electricity
The degree of freedom of electrical automobile two-shift automatic speed variator is 1, is in two gears, power from power shaft through the second cylindrical gear pair,
First jackshaft, the second torque transmitter, the second jackshaft and the 3rd cylindrical gear pair are transferred to differential assembly,
Power shaft and the gear ratio that ratio is two gears of the 3rd cylindrical gear pair driven gear rotating speed；
4) wherein, when power shaft rotates forward, a described gear and two gears are forward gear and two gears that advance；When power shaft is reverse
During rotation, a described gear and two gears are a gear and two gears.Described forward gear is identical with the gear ratio of one gear,
It is 7～17；Described advance two gear is identical with the gear ratio of two gears, is 3～13.
(3) advantage
1) present configuration is the compactest, lighter weight, and manufacturing cost can be greatly reduced；
2) present invention uses two-gear automatic speed changing, expands gear range, can be greatly reduced the performance requirement driving motor,
Allow to use high efficiency, light-weighted driving motor, reduce further pure electric automobile power drive system cumulative volume,
Gross mass, totle drilling cost；
3) present configuration is the compactest, stable drive, gear range width, pure electric automobile both can have been made to obtain the most dynamic
Power performance, it is also possible to allow motor operate in high efficient area more, reduce energy consumption, increases continual mileage, carries
The dynamic property of high car load and economy；
4) transmission loss of each gear of the present invention is the least, possesses high power transfer efficiency；
5) the second cylindrical gear pair driving gear of the present invention is fixing with power shaft is connected, and the second cylindrical gear pair driving gear manufactures
Assembling is easier to, and cost is lower, is more beneficial for the second cylindrical gear pair and obtains relatively big speed ratio；
6) all torque transmitters of the present invention can be selectively engaged, and required torque capacity is less, advantageously reduces and turns
The abrasion of square transfer device, and be conducive to reducing the size of torque transmitter, reduce pure electric automobile electricity further
The cumulative volume of drive system, gross mass, totle drilling cost.
Accompanying drawing explanation
Fig. 1 is the structural representation of embodiments of the invention 1
Fig. 2 is the structural representation of embodiments of the invention 2
Fig. 3 is the structural representation of embodiments of the invention 3
Fig. 4 is the structural representation of embodiments of the invention 4
In figure, sequence number, symbol, code name, unit are described as follows:
1 power shaft；2 first jackshafts；3 second jackshafts；4 first cylindrical gear pair driving gears；5 first cylindrical gear pairs
Driven gear；6 second cylindrical gear pair driving gears；7 second cylindrical gear pair driven gears；8 the 3rd cylindrical gear pair masters
Moving gear；9 the 3rd cylindrical gear pair driven gears；10 first torque transmitter drive ends；11 first torque transmitters
Driven end；12 second torque transmitter drive ends；13 second torque transmitter driven ends；14 differential assemblies；G1
One cylindrical gear pair；G2 the second cylindrical gear pair；G3 the 3rd cylindrical gear pair；C1 the first torque transmitter；C2
Two torque transmitters.
Detailed description of the invention
Embodiment 1, as it is shown in figure 1, one pure electric automobile two-shift automatic speed variator of the present invention, comprises power shaft 1, first
Jackshaft the 2, second jackshaft the 3, first cylindrical gear pair G1, the second cylindrical gear pair G2, the 3rd cylindrical gear pair G3,
First torque transmitter C1, the second torque transmitter C2, and differential assembly 14.Wherein:
1) described power shaft 1 cross section is circular；
2) described first jackshaft 2 cross section is circular；
3) described second jackshaft 3 cross section is circular；
4) described first cylindrical gear pair G1 is that helical gears are secondary, including the first cylindrical gear pair driving gear 4 and first
Cylindrical gear pair driven gear 5；
5) described second cylindrical gear pair G2 is that helical gears are secondary, including the second cylindrical gear pair driving gear 6 and second
Cylindrical gear pair driven gear 7；
6) described 3rd cylindrical gear pair G3 is that helical gears are secondary, including the 3rd cylindrical gear pair driving gear 8 and the 3rd
Cylindrical gear pair driven gear 9；
7) described first torque transmitter C1 is multiple-piece wet clutch, including the first torque transmitter drive end 10
With the first torque transmitter driven end 11, wherein, described first torque transmitter drive end 10 and the first torque
Transfer device driven end 11 can be selectively engaged, by temporary to power shaft 1 and the first cylindrical gear pair driving gear 4
Time couple together；
8) described second torque transmitter C2 is multiple-piece wet clutch, including the second torque transmitter drive end 12
With the second torque transmitter driven end 13, wherein, described second torque transmitter drive end 12 and the second torque
Transfer device driven end 13 can be selectively engaged, and the first jackshaft 2 and the second jackshaft 3 is temporarily connected
Get up；
9) described differential assembly 14 selects Santana 2000 Car differential mechanism.
Mutual relation prioritization scheme between them is:
1) rotation centerline of described power shaft the 1, second jackshaft 3 and differential assembly 14 is parallel to each other；
2) described power shaft the 1, first torque transmitter C1, the first cylindrical gear pair driving gear 4 and the second roller gear
The rotation centerline of secondary driving gear 6 overlaps；
3) described first jackshaft the 2, second jackshaft the 3, second torque transmitter C2, the first cylindrical gear pair driven gear
5, the rotation centerline of the second cylindrical gear pair driven gear 7 and the 3rd cylindrical gear pair driving gear 8 overlaps；
4) rotation centerline of described differential assembly 14 and the 3rd cylindrical gear pair driven gear 9 overlaps；
5) described power shaft 1 is fixing with the first torque transmitter drive end 10 is connected；
6) described power shaft 1 is fixing with the second cylindrical gear pair driving gear 6 is connected；
7) described first jackshaft 2 is fixing with the second cylindrical gear pair driven gear 7 is connected；
8) described first jackshaft 2 is fixing with the second torque transmitter drive end 12 is connected；
9) described second jackshaft 3 is fixing with the first cylindrical gear pair driven gear 5 is connected；
10) described second jackshaft 3 is fixing with the second torque transmitter driven end 13 is connected；
11) described second jackshaft 3 is fixing with the 3rd cylindrical gear pair driving gear 8 is connected；
12) shell and the 3rd cylindrical gear pair driven gear 9 of described differential assembly 14 is fixed and is connected；
13) described first cylindrical gear pair driving gear 4 is fixing with the first torque transmitter driven end 11 is connected；
14) described first cylindrical gear pair driving gear 4 empty set is on power shaft 1；
15) described first torque transmitter C1, first cylindrical gear pair driving gear the 4, second cylindrical gear pair driving gear 6
The rotation centerline of power shaft 1 is arranged in order to away from input near input, described 3rd cylinder
Gear pair driving gear the 8, first cylindrical gear pair driven gear the 5, second torque transmitter C2, the second cylinder
Gear pair driven gear 7 depends on to away from input near input on the rotation centerline of the second jackshaft 3
Secondary arrangement.
Their design parameter is:
1) a diameter of 25 millimeters of described power shaft 1；
2) a diameter of 60 millimeters of described first jackshaft 2；
3) a diameter of 60 millimeters of described second jackshaft 3；
4) described first cylindrical gear pair G1, the second cylindrical gear pair G2 and the 3rd cylindrical gear pair G3 normal module are respectively
1.75 millimeters, 1.75 millimeters and 2.00 millimeters；
5) described first cylindrical gear pair driving gear the 4, second cylindrical gear pair driving gear 6 and the 3rd cylindrical gear pair are actively
Gear 8 number of teeth is respectively 29,37 and 39；
6) described first cylindrical gear pair driven gear the 5, second cylindrical gear pair driven gear 7 and the 3rd cylindrical gear pair are driven
Gear 9 number of teeth is respectively 100,92 and 98；
7) described first torque transmitter C1 and the second torque transmitter C2 torque capacity are respectively 330 Newton meters and 850
Newton meter.
The transmission scheme related in the present invention is by controlling described first torque transmitter C1's and the second torque transmitter C2
Engage or separate, produce a gear and two two gears of gear.The brief introduction of work principle of the present invention is as follows:
1) when described first torque transmitter C1 and the second torque transmitter C2 is all in released state, this is pure electronic
The degree of freedom of automobile two-shift automatic speed variator is 2, and power cannot be transferred to differential assembly 14 from power shaft 1；
2) when described first torque transmitter C1 be in engagement state, the second torque transmitter C2 be in released state time,
The degree of freedom of this pure electric automobile two-shift automatic speed variator is 1, is in a gear, power from power shaft 1 through first turn
Square transfer device C1, the first cylindrical gear pair G1, that the second jackshaft 3 and the 3rd cylindrical gear pair G3 is transferred to is poor
Speed device assembly 14, power shaft 1 and the gear ratio that ratio is a gear of the 3rd cylindrical gear pair driven gear 9 rotating speed；
3) when described second torque transmitter C2 be in engagement state, the first torque transmitter C1 be in released state time,
The degree of freedom of this pure electric automobile two-shift automatic speed variator is 1, is in two gears, and power is round through second from power shaft 1
Stud wheel secondary G2, first jackshaft the 2, second torque transmitter C2, the second jackshaft 3 and the 3rd roller gear
Secondary G3 is transferred to differential assembly 14, and power shaft 1 with the ratio of the 3rd cylindrical gear pair driven gear 9 rotating speed is
The gear ratio of two gears；
4) wherein, when power shaft 1 rotates forward, a described gear and two gears are forward gear and two gears that advance；When power shaft 1
During reverse rotation, a described gear and two gears are a gear and two gears.Described forward gear and one gear ratio kept off
Identical, it is 8.6649；Described advance two gear is identical with the gear ratio of two gears, is 6.2481.
Embodiment 2, as in figure 2 it is shown, one pure electric automobile two-shift automatic speed variator of the present invention, comprises power shaft 1, first
Jackshaft the 2, second jackshaft the 3, first cylindrical gear pair G1, the second cylindrical gear pair G2, the 3rd cylindrical gear pair G3,
First torque transmitter C1, the second torque transmitter C2, and differential assembly 14.Wherein:
1) described power shaft 1 cross section is circular；
2) described first jackshaft 2 cross section is circular；
3) described second jackshaft 3 cross section is circular；
4) described first cylindrical gear pair G1 is that helical gears are secondary, including the first cylindrical gear pair driving gear 4 and first
Cylindrical gear pair driven gear 5；
5) described second cylindrical gear pair G2 is that helical gears are secondary, including the second cylindrical gear pair driving gear 6 and second
Cylindrical gear pair driven gear 7；
6) described 3rd cylindrical gear pair G3 is that helical gears are secondary, including the 3rd cylindrical gear pair driving gear 8 and the 3rd
Cylindrical gear pair driven gear 9；
7) described first torque transmitter C1 is multiple-piece wet clutch, including the first torque transmitter drive end 10
With the first torque transmitter driven end 11, wherein, described first torque transmitter drive end 10 and the first torque
Transfer device driven end 11 can be selectively engaged, by temporary to power shaft 1 and the first cylindrical gear pair driving gear 4
Time couple together；
8) described second torque transmitter C2 is multiple-piece wet clutch, including the second torque transmitter drive end 12
With the second torque transmitter driven end 13, wherein, described second torque transmitter drive end 12 and the second torque
Transfer device driven end 13 can be selectively engaged, and the first jackshaft 2 and the second jackshaft 3 is temporarily connected
Get up；
9) described differential assembly 14 selects Santana 2000 Car differential mechanism.
Mutual relation prioritization scheme between them is:
1) rotation centerline of described power shaft the 1, second jackshaft 3 and differential assembly 14 is parallel to each other；
2) described power shaft the 1, first torque transmitter C1, the first cylindrical gear pair driving gear 4 and the second roller gear
The rotation centerline of secondary driving gear 6 overlaps；
3) described first jackshaft the 2, second jackshaft the 3, second torque transmitter C2, the first cylindrical gear pair driven gear
5, the rotation centerline of the second cylindrical gear pair driven gear 7 and the 3rd cylindrical gear pair driving gear 8 overlaps；
4) rotation centerline of described differential assembly 14 and the 3rd cylindrical gear pair driven gear 9 overlaps；
5) described power shaft 1 is fixing with the first torque transmitter drive end 10 is connected；
6) described power shaft 1 is fixing with the second cylindrical gear pair driving gear 6 is connected；
7) described first jackshaft 2 is fixing with the second cylindrical gear pair driven gear 7 is connected；
8) described first jackshaft 2 is fixing with the second torque transmitter drive end 12 is connected；
9) described second jackshaft 3 is fixing with the first cylindrical gear pair driven gear 5 is connected；
10) described second jackshaft 3 is fixing with the second torque transmitter driven end 13 is connected；
11) described second jackshaft 3 is fixing with the 3rd cylindrical gear pair driving gear 8 is connected；
12) shell and the 3rd cylindrical gear pair driven gear 9 of described differential assembly 14 is fixed and is connected；
13) described first cylindrical gear pair driving gear 4 is fixing with the first torque transmitter driven end 11 is connected；
14) described first cylindrical gear pair driving gear 4 empty set is on power shaft 1；
15) described first cylindrical gear pair driving gear the 4, first torque transmitter C1, the second cylindrical gear pair driving gear 6
The rotation centerline of power shaft 1 is arranged in order to away from input near input, described 3rd cylinder
Gear pair driving gear the 8, first cylindrical gear pair driven gear the 5, second torque transmitter C2, the second cylinder
Gear pair driven gear 7 depends on to away from input near input on the rotation centerline of the second jackshaft 3
Secondary arrangement.
Their design parameter is:
1) a diameter of 25 millimeters of described power shaft 1；
2) a diameter of 60 millimeters of described first jackshaft 2；
3) a diameter of 60 millimeters of described second jackshaft 3；
4) described first cylindrical gear pair G1, the second cylindrical gear pair G2 and the 3rd cylindrical gear pair G3 normal module are respectively
1.75 millimeters, 1.75 millimeters and 2.00 millimeters；
5) described first cylindrical gear pair driving gear the 4, second cylindrical gear pair driving gear 6 and the 3rd cylindrical gear pair are actively
Gear 8 number of teeth is respectively 29,37 and 39；
6) described first cylindrical gear pair driven gear the 5, second cylindrical gear pair driven gear 7 and the 3rd cylindrical gear pair are driven
Gear 9 number of teeth is respectively 100,92 and 98；
7) described first torque transmitter C1 and the second torque transmitter C2 torque capacity are respectively 330 Newton meters and 850
Newton meter.
The transmission scheme related in the present invention is by controlling described first torque transmitter C1's and the second torque transmitter C2
Engage or separate, produce a gear and two two gears of gear.The brief introduction of work principle of the present invention is as follows:
1) when described first torque transmitter C1 and the second torque transmitter C2 is all in released state, this is pure electronic
The degree of freedom of automobile two-shift automatic speed variator is 2, and power cannot be transferred to differential assembly 14 from power shaft 1；
2) when described first torque transmitter C1 be in engagement state, the second torque transmitter C2 be in released state time,
The degree of freedom of this pure electric automobile two-shift automatic speed variator is 1, is in a gear, power from power shaft 1 through first turn
Square transfer device C1, the first cylindrical gear pair G1, that the second jackshaft 3 and the 3rd cylindrical gear pair G3 is transferred to is poor
Speed device assembly 14, power shaft 1 and the gear ratio that ratio is a gear of the 3rd cylindrical gear pair driven gear 9 rotating speed；
3) when described second torque transmitter C2 be in engagement state, the first torque transmitter C1 be in released state time,
The degree of freedom of this pure electric automobile two-shift automatic speed variator is 1, is in two gears, and power is round through second from power shaft 1
Stud wheel secondary G2, first jackshaft the 2, second torque transmitter C2, the second jackshaft 3 and the 3rd roller gear
Secondary G3 is transferred to differential assembly 14, and power shaft 1 with the ratio of the 3rd cylindrical gear pair driven gear 9 rotating speed is
The gear ratio of two gears；
4) wherein, when power shaft 1 rotates forward, a described gear and two gears are forward gear and two gears that advance；When power shaft 1
During reverse rotation, a described gear and two gears are a gear and two gears.Described forward gear and one gear ratio kept off
Identical, it is 8.6649；Described advance two gear is identical with the gear ratio of two gears, is 6.2481.
Embodiment 3, as it is shown on figure 3, one pure electric automobile two-shift automatic speed variator of the present invention, comprises power shaft 1, first
Jackshaft the 2, second jackshaft the 3, first cylindrical gear pair G1, the second cylindrical gear pair G2, the 3rd cylindrical gear pair G3,
First torque transmitter C1, the second torque transmitter C2, and differential assembly 14.Wherein:
1) described power shaft 1 cross section is circular；
2) described first jackshaft 2 cross section is circular；
3) described second jackshaft 3 cross section is circular；
4) described first cylindrical gear pair G1 is that helical gears are secondary, including the first cylindrical gear pair driving gear 4 and first
Cylindrical gear pair driven gear 5；
5) described second cylindrical gear pair G2 is that helical gears are secondary, including the second cylindrical gear pair driving gear 6 and second
Cylindrical gear pair driven gear 7；
6) described 3rd cylindrical gear pair G3 is that helical gears are secondary, including the 3rd cylindrical gear pair driving gear 8 and the 3rd
Cylindrical gear pair driven gear 9；
7) described first torque transmitter C1 is multiple-piece wet clutch, including the first torque transmitter drive end 10
With the first torque transmitter driven end 11, wherein, described first torque transmitter drive end 10 and the first torque
Transfer device driven end 11 can be selectively engaged, by temporary to power shaft 1 and the first cylindrical gear pair driving gear 4
Time couple together；
8) described second torque transmitter C2 is multiple-piece wet clutch, including the second torque transmitter drive end 12
With the second torque transmitter driven end 13, wherein, described second torque transmitter drive end 12 and the second torque
Transfer device driven end 13 can be selectively engaged, and the first jackshaft 2 and the second jackshaft 3 is temporarily connected
Get up；
9) described differential assembly 14 selects Santana 2000 Car differential mechanism.
Mutual relation prioritization scheme between them is:
1) rotation centerline of described power shaft the 1, second jackshaft 3 and differential assembly 14 is parallel to each other；
2) described power shaft the 1, first torque transmitter C1, the first cylindrical gear pair driving gear 4 and the second roller gear
The rotation centerline of secondary driving gear 6 overlaps；
3) described first jackshaft the 2, second jackshaft the 3, second torque transmitter C2, the first cylindrical gear pair driven gear
5, the rotation centerline of the second cylindrical gear pair driven gear 7 and the 3rd cylindrical gear pair driving gear 8 overlaps；
4) rotation centerline of described differential assembly 14 and the 3rd cylindrical gear pair driven gear 9 overlaps；
5) described power shaft 1 is fixing with the first torque transmitter drive end 10 is connected；
6) described power shaft 1 is fixing with the second cylindrical gear pair driving gear 6 is connected；
7) described first jackshaft 2 is fixing with the second cylindrical gear pair driven gear 7 is connected；
8) described first jackshaft 2 is fixing with the second torque transmitter drive end 12 is connected；
9) described second jackshaft 3 is fixing with the first cylindrical gear pair driven gear 5 is connected；
10) described second jackshaft 3 is fixing with the second torque transmitter driven end 13 is connected；
11) described second jackshaft 3 is fixing with the 3rd cylindrical gear pair driving gear 8 is connected；
12) shell and the 3rd cylindrical gear pair driven gear 9 of described differential assembly 14 is fixed and is connected；
13) described first cylindrical gear pair driving gear 4 is fixing with the first torque transmitter driven end 11 is connected；
14) described first cylindrical gear pair driving gear 4 empty set is on power shaft 1；
15) described first torque transmitter C1, first cylindrical gear pair driving gear the 4, second cylindrical gear pair driving gear 6
The rotation centerline of power shaft 1 is arranged in order to away from input near input, described first cylinder
Gear pair driven gear the 5, the 3rd cylindrical gear pair driving gear the 8, second torque transmitter C2, the second cylinder
Gear pair driven gear 7 depends on to away from input near input on the rotation centerline of the second jackshaft 3
Secondary arrangement.
Their design parameter is:
1) a diameter of 25 millimeters of described power shaft 1；
2) a diameter of 60 millimeters of described first jackshaft 2；
3) a diameter of 60 millimeters of described second jackshaft 3；
4) described first cylindrical gear pair G1, the second cylindrical gear pair G2 and the 3rd cylindrical gear pair G3 normal module are respectively
1.75 millimeters, 1.75 millimeters and 2.00 millimeters；
5) described first cylindrical gear pair driving gear the 4, second cylindrical gear pair driving gear 6 and the 3rd cylindrical gear pair are actively
Gear 8 number of teeth is respectively 29,37 and 39；
6) described first cylindrical gear pair driven gear the 5, second cylindrical gear pair driven gear 7 and the 3rd cylindrical gear pair are driven
Gear 9 number of teeth is respectively 100,92 and 98；
7) described first torque transmitter C1 and the second torque transmitter C2 torque capacity are respectively 330 Newton meters and 850
Newton meter.
The transmission scheme related in the present invention is by controlling described first torque transmitter C1's and the second torque transmitter C2
Engage or separate, produce a gear and two two gears of gear.The brief introduction of work principle of the present invention is as follows:
1) when described first torque transmitter C1 and the second torque transmitter C2 is all in released state, this is pure electronic
The degree of freedom of automobile two-shift automatic speed variator is 2, and power cannot be transferred to differential assembly 14 from power shaft 1；
2) when described first torque transmitter C1 be in engagement state, the second torque transmitter C2 be in released state time,
The degree of freedom of this pure electric automobile two-shift automatic speed variator is 1, is in a gear, power from power shaft 1 through first turn
Square transfer device C1, the first cylindrical gear pair G1, that the second jackshaft 3 and the 3rd cylindrical gear pair G3 is transferred to is poor
Speed device assembly 14, power shaft 1 and the gear ratio that ratio is a gear of the 3rd cylindrical gear pair driven gear 9 rotating speed；
3) when described second torque transmitter C2 be in engagement state, the first torque transmitter C1 be in released state time,
The degree of freedom of this pure electric automobile two-shift automatic speed variator is 1, is in two gears, and power is round through second from power shaft 1
Stud wheel secondary G2, first jackshaft the 2, second torque transmitter C2, the second jackshaft 3 and the 3rd roller gear
Secondary G3 is transferred to differential assembly 14, and power shaft 1 with the ratio of the 3rd cylindrical gear pair driven gear 9 rotating speed is
The gear ratio of two gears；
4) wherein, when power shaft 1 rotates forward, a described gear and two gears are forward gear and two gears that advance；When power shaft 1
During reverse rotation, a described gear and two gears are a gear and two gears.Described forward gear and one gear ratio kept off
Identical, it is 8.6649；Described advance two gear is identical with the gear ratio of two gears, is 6.2481.
Embodiment 4 as shown in Figure 4, one pure electric automobile two-shift automatic speed variator of the present invention, comprise power shaft 1, first
Jackshaft the 2, second jackshaft the 3, first cylindrical gear pair G1, the second cylindrical gear pair G2, the 3rd cylindrical gear pair G3,
First torque transmitter C1, the second torque transmitter C2, and differential assembly 14.Wherein:
1) described power shaft 1 cross section is circular；
2) described first jackshaft 2 cross section is circular；
3) described second jackshaft 3 cross section is circular；
4) described first cylindrical gear pair G1 is that helical gears are secondary, including the first cylindrical gear pair driving gear 4 and first
Cylindrical gear pair driven gear 5；
5) described second cylindrical gear pair G2 is that helical gears are secondary, including the second cylindrical gear pair driving gear 6 and second
Cylindrical gear pair driven gear 7；
6) described 3rd cylindrical gear pair G3 is that helical gears are secondary, including the 3rd cylindrical gear pair driving gear 8 and the 3rd
Cylindrical gear pair driven gear 9；
7) described first torque transmitter C1 is multiple-piece wet clutch, including the first torque transmitter drive end 10
With the first torque transmitter driven end 11, wherein, described first torque transmitter drive end 10 and the first torque
Transfer device driven end 11 can be selectively engaged, by temporary to power shaft 1 and the first cylindrical gear pair driving gear 4
Time couple together；
8) described second torque transmitter C2 is multiple-piece wet clutch, including the second torque transmitter drive end 12
With the second torque transmitter driven end 13, wherein, described second torque transmitter drive end 12 and the second torque
Transfer device driven end 13 can be selectively engaged, and the first jackshaft 2 and the second jackshaft 3 is temporarily connected
Get up；
9) described differential assembly 14 selects Santana 2000 Car differential mechanism.
Mutual relation prioritization scheme between them is:
1) rotation centerline of described power shaft the 1, second jackshaft 3 and differential assembly 14 is parallel to each other；
2) described power shaft the 1, first torque transmitter C1, the first cylindrical gear pair driving gear 4 and the second roller gear
The rotation centerline of secondary driving gear 6 overlaps；
3) described first jackshaft the 2, second jackshaft the 3, second torque transmitter C2, the first cylindrical gear pair driven gear
5, the rotation centerline of the second cylindrical gear pair driven gear 7 and the 3rd cylindrical gear pair driving gear 8 overlaps；
4) rotation centerline of described differential assembly 14 and the 3rd cylindrical gear pair driven gear 9 overlaps；
5) described power shaft 1 is fixing with the first torque transmitter drive end 10 is connected；
6) described power shaft 1 is fixing with the second cylindrical gear pair driving gear 6 is connected；
7) described first jackshaft 2 is fixing with the second cylindrical gear pair driven gear 7 is connected；
8) described first jackshaft 2 is fixing with the second torque transmitter drive end 12 is connected；
9) described second jackshaft 3 is fixing with the first cylindrical gear pair driven gear 5 is connected；
10) described second jackshaft 3 is fixing with the second torque transmitter driven end 13 is connected；
11) described second jackshaft 3 is fixing with the 3rd cylindrical gear pair driving gear 8 is connected；
12) shell and the 3rd cylindrical gear pair driven gear 9 of described differential assembly 14 is fixed and is connected；
13) described first cylindrical gear pair driving gear 4 is fixing with the first torque transmitter driven end 11 is connected；
14) described first cylindrical gear pair driving gear 4 empty set is on power shaft 1；
15) described first cylindrical gear pair driving gear the 4, first torque transmitter C1, the second cylindrical gear pair driving gear 6
The rotation centerline of power shaft 1 is arranged in order to away from input near input, described first cylinder
Gear pair driven gear the 5, the 3rd cylindrical gear pair driving gear the 8, second torque transmitter C2, the second cylinder
Gear pair driven gear 7 depends on to away from input near input on the rotation centerline of the second jackshaft 3
Secondary arrangement.
Their design parameter is:
1) a diameter of 25 millimeters of described power shaft 1；
2) a diameter of 60 millimeters of described first jackshaft 2；
3) a diameter of 60 millimeters of described second jackshaft 3；
4) described first cylindrical gear pair G1, the second cylindrical gear pair G2 and the 3rd cylindrical gear pair G3 normal module are respectively
1.75 millimeters, 1.75 millimeters and 2.00 millimeters；
5) described first cylindrical gear pair driving gear the 4, second cylindrical gear pair driving gear 6 and the 3rd cylindrical gear pair are actively
Gear 8 number of teeth is respectively 29,37 and 39；
6) described first cylindrical gear pair driven gear the 5, second cylindrical gear pair driven gear 7 and the 3rd cylindrical gear pair are driven
Gear 9 number of teeth is respectively 100,92 and 98；
7) described first torque transmitter C1 and the second torque transmitter C2 torque capacity are respectively 330 Newton meters and 850
Newton meter.
The transmission scheme related in the present invention is by controlling described first torque transmitter C1's and the second torque transmitter C2
Engage or separate, produce a gear and two two gears of gear.The brief introduction of work principle of the present invention is as follows:
1) when described first torque transmitter C1 and the second torque transmitter C2 is all in released state, this is pure electronic
The degree of freedom of automobile two-shift automatic speed variator is 2, and power cannot be transferred to differential assembly 14 from power shaft 1；
2) when described first torque transmitter C1 be in engagement state, the second torque transmitter C2 be in released state time,
The degree of freedom of this pure electric automobile two-shift automatic speed variator is 1, is in a gear, power from power shaft 1 through first turn
Square transfer device C1, the first cylindrical gear pair G1, that the second jackshaft 3 and the 3rd cylindrical gear pair G3 is transferred to is poor
Speed device assembly 14, power shaft 1 and the gear ratio that ratio is a gear of the 3rd cylindrical gear pair driven gear 9 rotating speed；
3) when described second torque transmitter C2 be in engagement state, the first torque transmitter C1 be in released state time,
The degree of freedom of this pure electric automobile two-shift automatic speed variator is 1, is in two gears, and power is round through second from power shaft 1
Stud wheel secondary G2, first jackshaft the 2, second torque transmitter C2, the second jackshaft 3 and the 3rd roller gear
Secondary G3 is transferred to differential assembly 14, and power shaft 1 with the ratio of the 3rd cylindrical gear pair driven gear 9 rotating speed is
The gear ratio of two gears；
4) wherein, when power shaft 1 rotates forward, a described gear and two gears are forward gear and two gears that advance；When power shaft 1
During reverse rotation, a described gear and two gears are a gear and two gears.Described forward gear and one gear ratio kept off
Identical, it is 8.6649；Described advance two gear is identical with the gear ratio of two gears, is 6.2481.
Finally illustrating, above example is only in order to illustrate technical scheme and unrestricted, although with reference to preferably implementing
The present invention has been described in detail by example, it will be understood by those within the art that, can enter technical scheme
Row amendment or equivalent, without deviating from objective and the scope of technical solution of the present invention, it all should contain the right in the present invention
In the middle of claimed range.
Claims (4)
1. a pure electric automobile two-shift automatic speed variator, it is characterised in that: it comprises power shaft, the first jackshaft, the second centre
Axle, the first cylindrical gear pair, the second cylindrical gear pair, the 3rd cylindrical gear pair, the first torque transmitter, the second torque pass
Delivery device, and differential assembly；Wherein:
1) described power shaft cross section is circular；
2) described first jackshaft cross section is circular；
3) described second jackshaft cross section is circular；
4) one during described first cylindrical gear pair is straight spur gear pair and helical gears pair, including the first Cylinder Gear
Wheel set driving gear and the first cylindrical gear pair driven gear；
5) one during described second cylindrical gear pair is straight spur gear pair and helical gears pair, including the second Cylinder Gear
Wheel set driving gear and the second cylindrical gear pair driven gear；
6) one during described 3rd cylindrical gear pair is straight spur gear pair and helical gears pair, including the 3rd Cylinder Gear
Wheel set driving gear and the 3rd cylindrical gear pair driven gear；
7) one during described first torque transmitter is clutch, lock unit and clutch collar three, including the first torque transmission
Device drive end and the first torque transmitter driven end, wherein, described first torque transmitter drive end and
One torque transmitter driven end can be selectively engaged, by temporary transient to power shaft and the first cylindrical gear pair driving gear
Couple together；
8) one during described second torque transmitter is clutch, lock unit and clutch collar three, including the second torque transmission
Device drive end and the second torque transmitter driven end, wherein, described second torque transmitter drive end and
Two torque transmitter driven ends can be selectively engaged, and the first jackshaft and the second jackshaft has temporarily been connected
Come；
Mutual relation between them is:
1) rotation centerline of described power shaft, the second jackshaft and differential assembly is parallel to each other；
2) described power shaft, the first torque transmitter, the first cylindrical gear pair driving gear and the second cylindrical gear pair driving tooth
The rotation centerline of wheel overlaps；
3) described first jackshaft, the second jackshaft, the second torque transmitter, the first cylindrical gear pair driven gear, second
The rotation centerline of cylindrical gear pair driven gear and the 3rd cylindrical gear pair driving gear overlaps；
4) rotation centerline of described differential assembly and the 3rd cylindrical gear pair driven gear overlaps；
5) described power shaft and the fixing connection of the first torque transmitter drive end；
6) described power shaft and the fixing connection of the second cylindrical gear pair driving gear；
7) described first jackshaft and the fixing connection of the second cylindrical gear pair driven gear；
8) described first jackshaft and the fixing connection of the second torque transmitter drive end；
9) described second jackshaft and the fixing connection of the second torque transmitter driven end；
10) described second jackshaft and the fixing connection of the first cylindrical gear pair driven gear；
11) described second jackshaft and the fixing connection of the 3rd cylindrical gear pair driving gear；
12) shell and the 3rd cylindrical gear pair driven gear of described differential assembly is fixed and is connected；
13) described first cylindrical gear pair driving gear and the fixing connection of the first torque transmitter driven end；
14) described first cylindrical gear pair driving gear empty set is on power shaft；
15) described first torque transmitter, the first cylindrical gear pair driving gear, the second cylindrical gear pair driving gear are in input
It is arranged in order to away from input near input on the rotation centerline of axle, described 3rd cylindrical gear pair master
Moving gear, the first cylindrical gear pair driven gear, the second torque transmitter, the second cylindrical gear pair driven gear
The rotation centerline of the second jackshaft is arranged in order to away from input near input；
Their design parameter is:
1) described power shaft diameter is not more than 200 millimeters；
2) described first jackshaft diameter is not more than 200 millimeters；
3) described second jackshaft diameter is not more than 200 millimeters；
4) described first cylindrical gear pair, the second cylindrical gear pair and the 3rd cylindrical gear pair normal module are not more than 10.00 millimeters；
5) described first cylindrical gear pair driving gear, the second cylindrical gear pair driving gear and the 3rd cylindrical gear pair driving gear
The number of teeth is not more than 100；
6) described first cylindrical gear pair driven gear, the second cylindrical gear pair driven gear and the 3rd cylindrical gear pair driven gear
The number of teeth is not more than 200；
7) described first torque transmitter and the second torque transmitter torque capacity are not more than 2000 Newton meters.
A kind of pure electric automobile two-shift automatic speed variator the most according to claim 1, it is characterised in that: in described mutual pass
In system the 15th) item can also be: described first cylindrical gear pair driving gear, the first torque transmitter, the second cylinder
Gear pair driving gear on the rotation centerline of power shaft from being arranged in order to away from input near input, described the
Three cylindrical gear pair driving gears, the first cylindrical gear pair driven gear, the second torque transmitter, the second cylindrical gear pair
Driven gear is arranged in order to away from input near input on the rotation centerline of the second jackshaft.
A kind of pure electric automobile two-shift automatic speed variator the most according to claim 1, it is characterised in that: in described mutual pass
In system the 15th) item can also be: described first torque transmitter, the first cylindrical gear pair driving gear, the second cylinder
Gear pair driving gear on the rotation centerline of power shaft from being arranged in order to away from input near input, described the
One cylindrical gear pair driven gear, the 3rd cylindrical gear pair driving gear, the second torque transmitter, the second cylindrical gear pair
Driven gear is arranged in order to away from input near input on the rotation centerline of the second jackshaft.
A kind of pure electric automobile two-shift automatic speed variator the most according to claim 1, it is characterised in that: in described mutual pass
In system the 15th) item can also be: described first cylindrical gear pair driving gear, the first torque transmitter, the second cylinder
Gear pair driving gear on the rotation centerline of power shaft from being arranged in order to away from input near input, described the
One cylindrical gear pair driven gear, the 3rd cylindrical gear pair driving gear, the second torque transmitter, the second cylindrical gear pair
Driven gear is arranged in order to away from input near input on the rotation centerline of the second jackshaft.
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| CN102392883A (en) * | 2011-11-03 | 2012-03-28 | 上海中科深江电动车辆有限公司 | Two-gear electric control mechanical type automatic gearbox used for electric automobile |
| CN103987558B (en) * | 2011-11-26 | 2016-08-17 | 丰田自动车株式会社 | Vehicular electric driving means |
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