CN109340323A - The mixed dynamic speed change gear of off-axis formula P2 - Google Patents
The mixed dynamic speed change gear of off-axis formula P2 Download PDFInfo
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- CN109340323A CN109340323A CN201811437990.XA CN201811437990A CN109340323A CN 109340323 A CN109340323 A CN 109340323A CN 201811437990 A CN201811437990 A CN 201811437990A CN 109340323 A CN109340323 A CN 109340323A
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- Prior art keywords
- gear
- input shaft
- speed change
- synchronizer
- output
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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
- F16H3/085—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 with more than one output 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
- F16H3/091—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 including a single countershaft
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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
- F16H3/12—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 with means for synchronisation not incorporated in the clutches
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
- Hybrid Electric Vehicles (AREA)
Abstract
The present invention provides a kind of mixed dynamic speed change gears of off-axis formula P2, belong to technical field of automobile components.It solves the technical problems such as existing speed change gear axial distance is longer.The mixed dynamic speed change gear of this off-axis formula P2 includes including double clutch, driving motor, input shaft one and input shaft two are provided on double clutch, the gear 18 and gear 19 of independently power output are provided on the output shaft of driving motor, gear 18 and input shaft one are sequentially connected, and gear 19 and input shaft two are sequentially connected.Driving motor is not take up the axial space of speed change gear, and the size of driving motor is unrestricted, and the axial distance of speed change gear can be allowed to become shorter, and also smaller to the whole change of automobile.
Description
Technical field
The invention belongs to automobile component fields, are related to a kind of mixed dynamic speed change gear of off-axis formula P2.
Background technique
In face of increasingly serious environmental protection pressure, conventional fuel oil automobile is gradually replaced by new-energy automobile.Wherein,
Mixed electrical automobile is the new-energy automobile type currently greatly developed both at home and abroad, and wherein the mixed dynamic type of P2 is that each Automobile Enterprises selection is thrown
Enter the main Types of research and development and manufacture.Since the mixed dynamic type of P2 is to add motor in engine and speed changer, i.e., in automobile
During advance, motor and engine carry out power output simultaneously.
China's Patent Application Publication (notification number: CN203548725U；The day for announcing: 2014.4.16) in disclose a kind of tool
There are mixed dynamic double clutch gearboxes of duplicate gear.It includes first clutch and second clutch, is set in transmission housing body
It is equipped with the first output shaft and the second output shaft, it is axial defeated to first clutch and second clutch progress power by hybrid unit
Out.
Under this configuration, hybrid unit therein be only connected to two, four, six, reverse gear, needing to realize remaining gear
When mixing dynamic, needs the additional connection motor on input shaft to carry out mixed dynamic, will cause motor and and engine crankshaft in this way
To be coaxially disposed, additional increase engine size, so if to guarantee that the mixed dynamic output of full gear and size are smaller simultaneously,
There are technical difficulties.
Summary of the invention
The present invention addresses the above problems in the prior art, provides a kind of mixed dynamic speed change gear of off-axis formula P2, this hair
It is bright the technical problem to be solved is that: how in the case where the mixed dynamic output of full gear to make speed change gear size reduction.
Object of the invention can be realized by the following technical scheme:
A kind of mixed dynamic speed change gear of off-axis formula P2, including double clutch, driving motor, output shaft one and output shaft two, institute
State and be provided with input shaft one on double clutch, input shaft two, the input shaft one and input shaft two both with output shaft one and
Output shaft two is connected by power it is characterized in that, be provided with jackshaft on driving motor, is provided on the jackshaft and input shaft
Gear ten can be operated alone in the gear 18 of one transmission connection and the gear 19 being sequentially connected with input shaft two, the jackshaft
Eight or gear 19 move.
It, being capable of double clutches with the mutual cooperation of two input shafts and two output shafts in the power output of automobile power
In shift, power transmitting is smooth stablizes, based on the drive mechanism of double clutches, when output an only input shaft with
A piece output shaft cooperates, and therefore, this case can pass through independent sliding tooth by additional increase intermediate shaft structure, jackshaft
18 or gear 19 are taken turns, in this way in power supplement, the power of jackshaft is also only output to input shaft by gear 18
One or by the way that on 19 input shaft two of gear, jackshaft does not carry out power outputs to two input shafts simultaneously, in this way mixed
Original double clutch shifting structures are not changed when closing power output, jackshaft effectively plays the role of auxiliary output.
And in additional increase structure, the axially compact structure of original double output shaft and dual input shaft is kept, it can be by jackshaft
It is arranged in gearbox side, does not increase the axial distance of gearbox additionally, keeps gearbox axial distance most short, to the whole of automobile
Structural reform is dynamic also smaller.
Synchronizer one, the synchronization are fixedly installed on the mixed dynamic speed change gear of above-mentioned off-axis formula P2, the jackshaft
Device one can be synchronous with gear 18 or the formation of gear 19 respectively.Synchronizer one can be to the gear 18 or gear on jackshaft
19 switch over, according to the switching for needing to carry out adaptability of automotive service gear, it is ensured that jackshaft is merely able to individually export
Gear 18 or individually output gear 19.
In the mixed dynamic speed change gear of above-mentioned off-axis formula P2, the mixed dynamic speed change gear further includes the gear for power output
16, be provided on the output shaft one with 16 meshed gears 14 of gear, be provided on the output shaft two and gear
Be provided with driven gear group on 16 meshed gears 15, the output shaft one and output shaft two, the input shaft one with
Driving gear group is provided on input shaft two, the gear 18 and gear 19 are sequentially connected in driving gear group.
The structure of two output shafts can cooperate the structure of two input shafts in double clutches, gear 14 and gear on two output shafts
15, which can stablize gear ten six of the driven for power output, exports.
In the mixed dynamic speed change gear of above-mentioned off-axis formula P2, the driven gear group include for a gear output gear five,
The gear seven of output is kept off for the gear eight of second gear output, for the gear six of three gear outputs, for four, for five gear outputs
Gear nine keeps off the gear 13 of output for six, for the gear 12 for output of reversing gear, the gear five, gear six, gear
Seven, gear eight is arranged on output shaft one, and the gear nine, gear 12, gear 13 are arranged on output shaft two, institute
State driving gear group include with nine meshed gears four of gear, with the gear three being driven of gear five, the tooth that is engaged with gear 13
17 and eight meshed gears one of gear are taken turns, the gear four, gear three and gear two are fixed on input shaft one,
The gear 17 is fixed on input shaft two with gear one.Gear in each driven gear group is respectively provided with correspondence
The gear of driving gear group engage, it is ensured that gear can stablize power transmission.
In the mixed dynamic speed change gear of above-mentioned off-axis formula P2, it is provided between the gear 18 and gear four for transmission
Gear 20 is provided with the gear 21 for transmission between the gear 19 and gear 17.Gear 20 and gear
21 structure can ensure on the dynamically stable input shaft for being transferred to double clutches of gear 18 and gear 19, and energy
Enough meet in installation space, driving motor gear is filled up with spatial joint clearance on double clutch input shafts.
It is coaxially connected between the gear 20 and gear 21 in the mixed dynamic speed change gear of above-mentioned off-axis formula P2.
Coaxially connected structure can guarantee that the rotation between gear 18 and gear 19 is relatively stable, and power output is smooth, and same
Axle construction can guarantee compact-sized, and cost is relatively low.
In the mixed dynamic speed change gear of above-mentioned off-axis formula P2, the gear four is located at one far from double clutch on input shaft one
End, the gear 17 are located at one end on input shaft two far from double clutch.The tooth that will be used to be connected by power with motor driven
The end position of input shaft is arranged with gear 17 for wheel four, can preferably balance the power input position on input shaft in this way,
End positions are power input site on input shaft, and middle position is power output position, power point on such input shaft
It dissipates uniformly, structure long-time stable.
Synchronized links gear five and gear are provided on the mixed dynamic speed change gear of above-mentioned off-axis formula P2, the output shaft one
The synchronizer three of six synchronizer two, synchronized links gear seven and gear eight is provided with synchronized links tooth on the output shaft two
Take turns nine synchronizer four, the synchronizer five of synchronized links gear 12 and gear 13.A synchronizer is arranged in every two gear
Structure can be improved the service efficiency of synchronizer, guarantee the structural compactness of speed change gear.
In the mixed dynamic speed change gear of above-mentioned off-axis formula P2, it is provided between the gear three and gear 12 for making power
Reversed gear ten and gear 11, the gear ten and gear 11 are coaxial arrangement, and the gear ten is engaged with gear three,
The gear 11 is engaged with gear 12.The steering of input shaft can be adjusted by gear ten and gear 11, Jin Erneng
Enough allow the output power of gear 16 contrary, vehicle can be realized retroversion.
Compared with prior art, the invention has the following advantages that
1, driving motor off-axis arranges that driving motor is not take up the axial space of speed changer, convenient for the axial direction of speed change gear
It reduces and does not influence interior other structures layout.
2, driving motor is as relatively small, the vehicle power that is not arranged in limitation suffered by its axial dimension of axial position
Plentifully, it transmits and stablizes in transmittance process, the gear for mixing dynamic output is more.
Detailed description of the invention
Fig. 1 is the structural schematic diagram of the present embodiment.
In figure, 1, driving motor；11, jackshaft；2, double clutches；21, input shaft one；22, input shaft two；31, output shaft
One；32, output shaft two；41, synchronizer one；42, synchronizer two；43, synchronizer three；44, synchronizer four；45, synchronizer five；
G1, gear one；G2, gear two；G3, gear three；G4, gear four；G5, gear five；G6, gear six；G7, gear seven；G8, gear
Eight；G9, gear nine；G10, gear ten；G11, gear 11；G12, gear 12；G13, gear 13；G14, gear 14；
G15, gear 15；G16, gear 16；G17, gear 17；G18, gear 18；G19, gear 19；G20, gear two
Ten；G21, gear 21.
Specific embodiment
Following is a specific embodiment of the present invention in conjunction with the accompanying drawings, technical scheme of the present invention will be further described,
However, the present invention is not limited to these examples.
As shown in Figure 1, a kind of mixed dynamic speed change gear of off-axis formula P2, including double clutch 2, driving motor 1, double clutch 2
On be provided with input shaft 1 and input shaft 2 22, driving motor 1 can carry out power to input shaft 1 and input shaft 2 22
Output.
It is provided with jackshaft 11 on driving motor 1, synchronizer 1,18 G18 of gear and tooth are provided on jackshaft 11
19 G19 are taken turns, synchronizer 1 can carry out powershift between 19 G19 of 18 G18 of gear and gear, and jackshaft 11 is logical
Crossing synchronizer 1, band 18 G18 of moving gear or 19 G19 of gear is rotated respectively, and 11 output points of jackshaft are gear 18
19 G19 of G18 or gear, jackshaft 11 can not allow 18 G18 of gear and 19 G19 of gear while to carry out power defeated
Out.
Mixed dynamic speed change gear further includes 16 G16 of gear, output shaft 1 and the output shaft 2 32 for power output, defeated
Be provided on shaft 1 with 16 G16 meshed gears of gear, 14 G14, be provided with and gear 16 on output shaft 2 32
15 G15 of G16 meshed gears, is provided with driven gear group on output shaft 1 and output shaft 2 32, input shaft 1 with
Driving gear group is provided on input shaft 2 22.Input shaft 1 and input shaft 22 pass through driving gear group and driven gear group
Cooperation so that power is transferred to output shaft 1 or output shaft 32 according to a certain percentage, and then pass through 16 G16 of gear
Complete power output.
Driven gear group includes five G5 of gear for a gear output, eight G8 of gear for second gear output, for three gears
Six G6 of gear of output, seven G7 of gear for four gear outputs, nine G9 of gear for five gear outputs, the tooth for keeping off output for six
13 G13, ten G12 of gear for output of reversing gear are taken turns, five G5 of gear, six G6 of gear, seven G7 of gear, eight G8 of gear are arranged at
On output shaft 1, nine G9 of gear, ten G12 of gear, 13 G13 of gear are arranged on output shaft 2 32.
Wherein, synchronizer 42, the synchronized links of five G5 of synchronized links gear Yu six G6 of gear are provided on output shaft 1
The synchronizer 3 43 of seven G7 of gear and eight G8 of gear are provided with the synchronizer four of nine G9 of synchronized links gear on output shaft 2 32
44, the synchronizer 5 45 of ten G12 of synchronized links gear and 13 G13 of gear.Gear may be implemented by the switching of synchronizer 42
Power transmission on six G6 of five G5 or gear can similarly obtain synchronizer 3 43, synchronizer 4 44, synchronizer to output shaft 1
5 45.
Three G3 of gear and tooth that driving gear group includes and nine G9 meshed gears of gear, four G4 and five G5 of gear is driven
Take turns 13 G13 meshed gears, 17 G17 and eight G8 meshed gears of gear, one G1, four G4 of gear, gear three G3 and gear G2
It is fixed on input shaft 1,17 G17 of gear and one G1 of gear are fixed on input shaft 2 22.
Wherein, ten G10 of gear and gear 11 for making power reverse are provided between ten G12 of three G3 of gear and gear
G11, ten G10 of gear and 11 G11 of gear are coaxial arrangement, and ten G10 of gear is engaged with three G3 of gear, 11 G11 of gear and tooth
Take turns 12 G12 engagement.12 G12 of gear can be allowed to the dynamic of output shaft 2 32 by 11 G11 of gear and ten G10 structure of gear
Power reversely exports.
18 G18 of gear and 19 G19 of gear of jackshaft 11 are carried out in the transmittance process of power output, gear 18
G18 is transmitted power on four G4 of gear, and 19 G19 of gear is transmitted power on 17 G17 of gear, 18 G18 of gear with
It is provided with 20 G20 of gear for transmission between four G4 of gear, is arranged between 17 G17 of 19 G19 of gear and gear useful
It is coaxially connected between 21 G21 of gear of transmission, 21 G21 of 20 G20 of gear and gear.Due to driving motor 1
On gear be difficult to directly assemble be fixed to input shaft gear on, pass through the connection of 20 G20 of gear and 21 G21 of gear
Meet the requirement of installation connection.
Wherein, it is located at one end on input shaft 1 far from double clutch 2, Yi Jichi for four G4 of the gear of power transmission
One end that 17 G17 are located at separate double clutch 2 on input shaft 2 22 is taken turns, one G1 of gear is located at the interposition of input shaft 2 22
It sets, three G3 of gear and two G2 of gear is located at the middle position of input shaft 1.
The gear situation of the speed change gear is as follows:
1 gear operating condition: double clutch 2 is combined and is separated with input shaft 2 22, synchronizer 1 and gear with output shaft 1
18 G18 are combined, and synchronizer 2 42 and five G5 of gear are combined.
1 gear engine power transfer route: engine → three G3 of double clutch 2 → input shaft, one 21 → gear → gear five
G5 → 14 G14 of synchronizer 2 42 → output shaft, one 31 → gear → 16 G16 of gear.
1 gear motor power transfer route: 18 G18 of driving motor 1 → synchronizer, one 41 → gear → 20 G20 of gear →
Four G4 of gear → one 21 → gear of input shaft, three G3 → five G5 of gear → 2 42 → output shaft of synchronizer, one 31 → gear, 14 G14
16 G16 of → gear.
2 gear operating conditions: double clutch 2 is combined and is separated with input shaft 1, synchronizer 1 and gear with output shaft 2 32
19 G19 are combined, and synchronizer 3 43 and eight G8 of gear are combined.
2 gear engine power transfer routes: engine → one G1 of double clutch 2 → input shaft, 2 22 → gear → gear eight
G8 → 14 G14 of synchronizer 3 43 → output shaft, one 31 → gear → 16 G16 of gear.
2 gear motor power transfer routes: 19 G19 of driving motor 1 → synchronizer, one 41 → gear → 21 G21 of gear
17 G17 of → gear → 2 22 → gear of input shaft, one G1 → eight G8 of gear → 3 43 → output shaft of synchronizer, one 31 → gear ten
Four G14 → gear 16.
3 gear operating conditions: double clutch 2 is combined and is separated with input shaft 2 22, synchronizer 1 and gear with output shaft 1
18 combine, and synchronizer 2 42 and six G6 of gear are combined.
3 gear engine power transfer routes: engine → three G3 of double clutch 2 → input shaft, one 21 → gear → gear six
G6 → 14 G14 of synchronizer 2 42 → output shaft, one 31 → gear → 16 G16 of gear.
3 gear motor power transfer routes: 18 G18 of driving motor 1 → synchronizer, one 41 → gear → 20 G20 of gear →
Four G4 of gear → one 21 → gear of input shaft, two G2 → six G6 of gear → 2 42 → output shaft of synchronizer, one 31 → gear, 14 G14
16 G16 of → gear.
4 gear operating conditions: double clutch 2 is combined and is separated with input shaft 1, synchronizer 1 and gear with output shaft 2 32
19 G19 are combined, and synchronizer 3 43 and seven G7 of gear are combined.
4 gear engine power transfer routes: engine → 17 G17 of double clutch 2 → input shaft, 2 22 → gear → tooth
Take turns seven G7 → 14 G14 of synchronizer 3 43 → output shaft, one 31 → gear → 16 G16 of gear.
4 gear motor power transfer routes: 19 G19 of driving motor 1 → synchronizer, one 41 → gear → 21 G21 of gear
17 G17 of → gear → 2 22 → gear of input shaft, 17 G17 → seven G7 of gear → synchronizer 3 43 → output shaft, one 31 → tooth
Take turns 14 G14 → gear, 16 G16.
5 gear operating conditions: double clutch 2 is combined and is separated with input shaft 2 22, synchronizer 1 and gear with output shaft 1
18 G18 are combined, and synchronizer 4 44 and nine G9 of gear are combined.
5 gear engine power transfer routes: engine → four G4 of double clutch 2 → input shaft, one 21 → gear → gear nine
G9 → 15 G15 of synchronizer 4 44 → output shaft, 2 32 → gear → 16 G16 of gear.
5 gear motor power transfer routes: 18 G18 of driving motor 1 → synchronizer, one 41 → gear → 20 G20 of gear →
Four G4 of gear → nine G9 of gear → 15 G15 of synchronizer 4 44 → output shaft, 2 32 → gear → 16 G16 of gear.
6 gear operating conditions: double clutch 2 is combined and is separated with input shaft 1, synchronizer 1 and gear with output shaft 2 32
19 G19 are combined, and synchronizer 5 45 and 13 G13 of gear are combined.
6 gear engine power transfer routes: engine → 17 G17 of double clutch 2 → input shaft, 2 22 → gear → tooth
Take turns 13 G13 → 15 G15 of synchronizer 5 45 → output shaft, 2 32 → gear → 16 G16 of gear.
6 gear motor power transfer routes: 19 G19 of driving motor 1 → synchronizer, one 41 → gear → 21 G21 of gear
17 G17 of → gear → 13 G13 of gear → 15 G15 of synchronizer 5 45 → output shaft, 2 32 → gear → 16 G16 of gear.
R keeps off operating condition: double clutch 2 is combined and is separated with input shaft 2 22, synchronizer 1 and gear with output shaft 1
18 G18 are combined, and synchronizer 5 45 and 12 G12 of gear are combined.
Reverse gear engine power transmission line: engine → three G3 of double clutch 2 → input shaft, one 21 → gear → gear
Ten G10 → 11 G11 of gear → 12 G12 of gear → 15 G15 of synchronizer 5 45 → output shaft, 2 32 → gear → gear ten
Six G16.
Reverse gear motor power transfer route: 18 G18 of driving motor 1 → synchronizer, one 41 → gear → 20 G20 of gear
Four G4 of → gear → one 21 → gear of input shaft, three G3 → ten G10 of gear → 11 G11 of gear → 12 G12 of gear → synchronizer
5 45 → output shaft, 2 32 → gear, 15 G15 → 16 G16 of gear.
Specific embodiment described herein is only an example for the spirit of the invention.The neck of technology belonging to the present invention
The technical staff in domain can make various modifications or additions to the described embodiments or replace by a similar method
In generation, however, it does not deviate from the spirit of the invention or beyond the scope of the appended claims.
Although 1, driving motor is used more herein；11, jackshaft；2, double clutches；21, input shaft one；22, it inputs
Axis two；31, output shaft one；32, output shaft two；41, synchronizer one；42, synchronizer two；43, synchronizer three；44, synchronizer four；
45, synchronizer five；G1, gear one；G2, gear two；G3, gear three；G4, gear four；G5, gear five；G6, gear six；G7, tooth
Wheel seven；G8, gear eight；G9, gear nine；G10, gear ten；G11, gear 11；G12, gear 12；G13, gear 13；
G14, gear 14；G15, gear 15；G16, gear 16；G17, gear 17；G18, gear 18；G19, gear ten
Nine；G20, gear 20；The first-class term of G21, gear 20, but it does not exclude the possibility of using other terms.Use these
Term is only for the convenience of describing and explaining the nature of the invention；It is construed as any additional limitation all
It is to be disagreed with spirit of that invention.
Claims (9)
1. a kind of mixed dynamic speed change gear of off-axis formula P2, including double clutch (2), driving motor (1), output shaft one (31) and output
Axis two (32), is provided with input shaft one (21) and input shaft two (22) on the double clutch (2), the input shaft one (21) and
Input shaft two (22) is both connected by power with output shaft one (31) and output shaft two (32), which is characterized in that driving motor (1)
On be provided with jackshaft (11), be provided on the jackshaft (11) with input shaft one (21) transmission connection gear 18
(G18) and gear 18 can be operated alone in the gear 19 (G19) with input shaft two (22) transmission connection, the jackshaft (11)
(G18) or gear 19 (G19) moves.
2. the mixed dynamic speed change gear of off-axis formula P2 according to claim 1, which is characterized in that fixed on the jackshaft (11)
It is provided with synchronizer one (41), the synchronizer one (41) can form with gear 18 (G18) or gear 19 (G19) same respectively
Step.
3. the mixed dynamic speed change gear of off-axis formula P2 according to claim 2, which is characterized in that the mixed dynamic speed change gear also wraps
The gear 16 (G16) for power output is included, is provided with the tooth engaged with gear 16 (G16) on the output shaft one (31)
Take turns 14 (G14), be provided on the output shaft two (32) with gear 16 (G16) meshed gears 15 (G15), it is described defeated
Driven gear group is provided on shaft one (31) and output shaft two (32), on the input shaft one (21) and input shaft two (22)
It is provided with driving gear group, the gear 18 (G18) and gear 19 (G19) are sequentially connected in driving gear group.
4. the mixed dynamic speed change gear of off-axis formula P2 according to claim 3, which is characterized in that the driven gear group includes using
Gear five (G5) in a gear output, the gear eight (G8) for second gear output keep off the gear six (G6) of output for three, are used for
The gear seven (G7) of four gear outputs, the gear 13 (G13) for six gear outputs, is used the gear nine (G9) for five gear outputs
In the gear 12 (G12) for output of reversing gear, the gear five (G5), gear six (G6), gear seven (G7), gear eight (G8) are all provided with
It sets on output shaft one (31), the gear nine (G9), gear 12 (G12), gear 13 (G13) are arranged at output shaft two
(32) on, the driving gear group includes and gear nine (G9) meshed gears four (G4), the gear with gear five (G5) transmission
Three (G3) and gear 13 (G13) meshed gears 17 (G17) and gear eight (G8) meshed gears one (G1), the tooth
Four (G4) of wheel, gear three (G3) and gear two (G2) are fixed on input shaft one (21), the gear 17 (G17) with
Gear one (G1) is fixed on input shaft two (22).
5. the mixed dynamic speed change gear of off-axis formula P2 according to claim 4, which is characterized in that the gear 18 (G18) with
It is provided with the gear 20 (G20) for transmission between gear four (G4), the gear 19 (G19) and gear 17 (G17)
Between be provided with gear 21 (G21) for transmission.
6. the mixed dynamic speed change gear of off-axis formula P2 according to claim 5, which is characterized in that the gear 20 (G20) with
It is coaxially connected between gear 21 (G21).
7. the mixed dynamic speed change gear of off-axis formula P2 according to claim 4, which is characterized in that the gear four (G4) is located at defeated
Enter on axis one (21) far from double clutch (2) one end, the gear 17 (G17) be located on input shaft two (22) far from pair from
One end of clutch (2).
8. the mixed dynamic speed change gear of off-axis formula P2 according to claim 4, which is characterized in that set on the output shaft one (31)
It is equipped with the synchronizer two (42), synchronized links gear seven (G7) and gear eight of synchronized links gear five (G5) and gear six (G6)
(G8) synchronizer three (43), be provided on the output shaft two (32) synchronized links gear nine (G9) synchronizer four (44),
The synchronizer five (45) of synchronized links gear 12 (G12) and gear 13 (G13).
9. the mixed dynamic speed change gear of off-axis formula P2 according to claim 4, which is characterized in that the gear three (G3) and gear
The gear ten (G10) and gear 11 (G11) for making power reverse, the gear ten (G10) are provided between 12 (G12)
Be coaxial arrangement with gear 11 (G11), the gear ten (G10) engages with gear three (G3), the gear 11 (G11) and
Gear 12 (G12) engagement.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811437990.XA CN109340323B (en) | 2018-11-28 | 2018-11-28 | Eccentric shaft type P2 hybrid transmission device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811437990.XA CN109340323B (en) | 2018-11-28 | 2018-11-28 | Eccentric shaft type P2 hybrid transmission device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109340323A true CN109340323A (en) | 2019-02-15 |
| CN109340323B CN109340323B (en) | 2020-07-10 |
Family
ID=65318630
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201811437990.XA Active CN109340323B (en) | 2018-11-28 | 2018-11-28 | Eccentric shaft type P2 hybrid transmission device |
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