KR20150144368A - Double clutch transmission - Google Patents
Double clutch transmission Download PDFInfo
- Publication number
- KR20150144368A KR20150144368A KR1020140072634A KR20140072634A KR20150144368A KR 20150144368 A KR20150144368 A KR 20150144368A KR 1020140072634 A KR1020140072634 A KR 1020140072634A KR 20140072634 A KR20140072634 A KR 20140072634A KR 20150144368 A KR20150144368 A KR 20150144368A
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- KR
- South Korea
- Prior art keywords
- gear
- input shaft
- clutch
- restraining
- gears
- Prior art date
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Classifications
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D21/00—Systems comprising a plurality of actuated clutches
- F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
- F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/02—Arrangements for synchronisation, also for power-operated clutches
- F16D23/04—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch
- F16D23/06—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch and a blocking mechanism preventing the engagement of the main clutch prior to synchronisation
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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
- F16H3/093—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 with two or more countershafts
Abstract
A double clutch transmission is introduced.
To this end, the present invention provides a clutch device comprising: a clutch unit configured by a first clutch and a second clutch so that power can be selectively interrupted; A first input shaft provided with a plurality of speed change stage drive gears and directly connected to the first clutch; A third input shaft provided with a second input shaft and a second synchronous portion provided with a first synchronous portion that can be meshed with the plurality of speed change stage drive gears; And a fourth input shaft provided with a plurality of restraint gears so as to engage with a part of the plurality of speed change stage driving gears so as to reduce the length of the electric field and perform a speed change process.
Description
The present invention relates to a double clutch transmission, and more particularly, to a dual clutch transmission, which can reduce the length of the entire DCT by providing a separate input shaft for performing a shift operation before the conventional DCT structure is improved. And more particularly to a double clutch transmission capable of reducing the number of parts and increasing the speed change stage.
Generally, the double clutch transmission includes two clutches, so that the power transmitted to the gear train of the transmission can be independently transmitted through the two clutches. That is, the input shaft can be divided into two through two clutches, and the power transmitted from the two input shafts can be supplied to the alternating means and the alternating means, respectively, and the degrees of freedom So that the shift can be automatically performed.
On the other hand, since the double clutch transmission uses two clutches structurally, the total length of the transmission is inevitably relatively long.
Particularly, in recent years, the speed change stage at which the transmission is shifted gradually becomes shorter, the double clutch transmission may have an excessively long overall length of the transmission, so that it is weak in package performance of the transmission itself, .
FIG. 1 is a schematic view of a structure of a conventional seven-stage DCT. As shown in FIG. 1, a plurality of gears (19 in total) are required to implement a 7-speed DCT structure and four dog clutches have.
This increases the weight due to a plurality of gears, and increases the cost for installation. In addition, there is a problem that the number of actuators for operating the dog clutch increases in the dog clutch
In addition, due to the installation of the plurality of gears and the dog clutch, the overall structure of the DCT itself is increased, so that the package performance of the transmission itself is weakened and the mountability of the vehicle is deteriorated.
Various prior arts such as "Powertrain of double-clutch transmission" of Korean Patent Laid-Open Publication No. 10-2010-0064719 and "Hybrid Vehicle" of Japanese Laid-Open Patent Publication No. 2013-43478 are disclosed as related arts.
However, in the case of the "power train of the double clutch transmission ", the overall length of the transmission relatively short as compared with the transmission of the conventional 6-speed double clutch is realized to greatly improve the package performance of the transmission and the mountability to the vehicle, The cost, the weight and the volume of the transmission can be reduced by increasing the commerciality of the transmission and by not providing a separate reverse shaft for realizing the post-diagnosis. However, the number of dog clutches, which are still synchronization mechanisms, In addition, the present invention does not disclose a technical idea of performing a single shifting process before a synchronization process using a dog clutch by providing a separate input shaft as in the present invention, and it is a matter of course that such a double clutch transmission is mounted on a hybrid vehicle There is no disclosure of technical ideas for expanding the surname.
Further, in the case of the above-mentioned "hybrid vehicle ", it is possible to provide a hybrid vehicle capable of reliably starting the internal combustion engine when the air conditioner is operated during EV traveling. However, The technical idea of minimizing the total length of the DCT compared to the conventional hybrid vehicle or reducing the shift time by reducing the wear of the synchronizer of the dog clutch is not disclosed.
It should be understood that the foregoing description of the background art is merely for the purpose of promoting an understanding of the background of the present invention and is not to be construed as adhering to the prior art already known to those skilled in the art.
SUMMARY OF THE INVENTION In order to solve the above-described problems, the present invention provides a transmission having a relatively short gear ratio as compared with a conventional double clutch transmission having eight gear stages, thereby improving the package performance of the transmission and the vehicle loadability A double clutch transmission capable of reducing the number of gears required to reduce the number of gears and reducing the number of dog clutches as compared with the conventional 7-speed DCT, thereby reducing the number of dog clutch actuating actuators, The purpose of the transmission is to provide.
A double clutch transmission is introduced.
To this end, according to the present invention, there is provided a clutch device comprising: a clutch portion composed of a first clutch and a second clutch for selectively interrupting power; a first input shaft provided with a plurality of speed change stage drive gears and directly connected to the first clutch; A third input shaft provided with a second input shaft and a second synchronous portion provided with a first synchronous portion that can be meshed with the first drive gear, and a third shift shaft meshed with a portion of the plurality of speed change stage drive gears, And a fourth input shaft provided with a plurality of restraint gears.
A first restraining gear, a second restraining gear, a third restraining gear, and a first free gear are rotatably inserted into the first input shaft along a longitudinal direction of the first input shaft, and the first and second restraining gears are selectively The third clutch gear is engaged with a part of a plurality of restraint gears provided on the fourth input shaft to perform a shifting process and the second clutch is engaged with the first free gear, And the first input shaft is driven differently from the rotational speed of the engine through the second input shaft when the second clutch is engaged.
The first clutch is directly connected to the first input shaft and driven at the same speed as the number of revolutions of the engine at the time of engagement of the first clutch so that the first input shaft and the second input shaft are selectively engaged to implement a two- .
The fourth input shaft is directly connected to a fourth restraining gear and a fifth restraining gear of different sizes along the longitudinal direction of the fourth input shaft. The gear ratio of the fourth restraining gear and the third restraining gear, The fifth free gear and the first free gear have gear ratios different from each other.
The first synchronizing unit may include a second free gear disposed along a longitudinal direction of the second input shaft, a second dog clutch, and a third free gear, and a sixth restraining gear is disposed on one side of the second input shaft, The second synchronizer includes a fourth free gear, a third dog clutch, and a fifth free gear provided at corresponding positions of the first synchronizer and along the longitudinal direction of the third input shaft, And a seventh restraining gear is provided at a position corresponding to the restraining gear.
The sixth and seventh restraining gears are engaged with the driving gear to transmit power to the driving shaft.
The second and third dog clutches selectively selectively couple the second freewheel gear and the first and second free gears, or the first and second freewheeling gears, When the power is transmitted to the drive shaft or when the second and third dog clutches selectively selectively engage the third and fifth freewheels, the third freewheel gear, the second restraining gear, the third freewheel gear and the fifth freewheel gear The power of the first input shaft is transmitted to the drive shaft so that the gear ratio of the two stages is realized by the clutch portion and the gear ratios of the four stages are realized by the first and second synchronizer portions, .
Further comprising a fifth input shaft provided with a sixth freewheel, a fourth dog clutch and a rotary gear in the longitudinal direction thereof such that a reverse drive is realized, the sixth freewheel being engaged with the third restraining gear, Is engaged with the seventh constraining gear.
On the other hand, a hybrid vehicle equipped with a double clutch transmission is also introduced.
To this end, according to the present invention, there is provided a clutch device comprising: a clutch portion composed of a first clutch and a second clutch for selectively interrupting power; a first input shaft provided with a plurality of speed change stage drive gears and directly connected to the first clutch; A third input shaft provided with a second input shaft and a second synchronous portion provided with a first synchronizing portion that can be meshed with the first driving gear, a second synchronizing portion provided with the connecting gear unit, and a third input shaft, A fourth input shaft provided with a plurality of restraint gears for performing a shifting process, and a motor directly connected to one side of the second input shaft.
The connecting gear unit is a restraining gear, and when the first clutch and the second clutch are disengaged, the motor is driven to enable EV traveling.
The connecting gear unit is composed of a seventh freewheel gear and a fifth dog clutch, and when the fifth dog clutch is released, the power of the motor is not transmitted to the drive shaft, so that the vehicle can be charged while the vehicle is stopped.
The present invention also provides a clutch device comprising a clutch portion composed of a first clutch and a second clutch and a first input shaft provided with a plurality of speed change stage drive gears and directly connected to the first clutch so that power can be selectively interrupted, A third input shaft provided with a second input shaft and a second synchronous portion provided with a first synchronous portion that can be meshed with the first drive gear, and a third shift shaft engaged with a portion of the plurality of speed change stage drive gears so as to reduce the length of the total length, A fourth input shaft provided with a plurality of restraint gears and a double clutch transmission implemented such that the motor can be directly connected to one side of the first input shaft so that the vehicle can be charged while the vehicle is stationary.
According to the double clutch transmission structure of the present invention having the above-described configuration, the following various effects are realized.
First, there is an advantage that the electric field of the relatively short transmission is realized as compared with the conventional 7-speed double clutch transmission.
Second, the short range of the transmission is realized, which improves the package performance of the transmission and the mountability to the vehicle.
Thirdly, there is an advantage that the number of dog clutches to be used is reduced compared to a conventional double clutch transmission, thereby reducing the number of dog clutch actuating actuators, thereby realizing cost reduction.
Fourth, various effects can be realized by installing a double clutch transmission according to the present invention in a hybrid vehicle and providing a double clutch transmission structure for a hybrid vehicle capable of charging the vehicle during stopping as well as EV driving.
BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a diagram showing a conventional seven-stage DCT structure.
2 is a view showing a structure of a double clutch transmission according to the present invention.
3 is a view showing a power transmission path of a double clutch transmission according to the present invention.
4 is a view for explaining the difference between the present invention and a conventional double clutch transmission;
5 is a first embodiment in which the double clutch transmission according to the present invention is mounted on a hybrid vehicle.
BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, a preferred embodiment of a double clutch transmission according to the present invention will be described with reference to the accompanying drawings.
As shown in the figure, the present invention mainly includes a
The
A
As will be described in detail below, the plurality of speed-change drive gears include a
On the other hand, the restraint gear is a gear in which gears are restrained with respect to a shaft on which the gear is mounted and the rotational force can be transmitted to each other continuously, and the free gear is a gear The relative rotation of the gear with respect to the rotation direction is basically possible.
That is, the restraint gear may be formed integrally with the shaft, assembled with a spline, a key, etc., and the free gear may be assembled to the shaft by a bush or a bearing.
The
As shown in the drawing, the present invention is characterized in that a
A
With this structure, when the
That is, in the related art, since the
For example, the fourth
As described above, the
At this time, the
Of course, the
That is, the first and
The
For example, as will be described later in detail, the
The
The
This will be described in detail as follows.
When the
The
On the other hand, as described above, the fourth and
The gear ratio of the
Referring again to FIG. 2, the
The
That is, the
The
In the case of the first and second stages, the sleeve of the
The
When the second and
That is, the sleeve of the
Similarly, when the second and
That is, in the case of the fifth and sixth stages, the sleeve of the
With this configuration, the gear ratio of the two stages is realized by the
The present invention further includes a
With this configuration, when the sleeve of the
FIG. 3 is a view showing an operation state of the first to fourth stages of the double clutch transmission according to the present invention. Hereinafter, the power transmission path of the powertrain of the double clutch type transmission according to the present invention will be described as follows.
3 (a) is a diagram showing a first stage. In the first stage, the sleeve of the
Fig. 3 (b) is a diagram showing the two-stage state. In the two-stage state, the
In this case, the power of the engine is transmitted to the
The first through fourth
3 (c) is a diagram showing a three-stage state in which the
Thereafter, the
The second
On the other hand, the shifting by the dog clutch is the same as the shifting of the AMT and the MT, and the power transmission is interrupted while the
However, according to the present invention, a
In addition, 50% of the shifting occurs in the same manner as the DCT, and shifting by the second and third dog clutch occurs in the third and subsequent stages. Therefore, there is an advantage that the inertia of the vehicle is sufficient and a bad shifting feeling can be minimized.
3 (d) is a diagram showing a four-stage state. As in the process of shifting from the first stage to the second stage, the
In this case, the power of the engine is transmitted to the
On the other hand, when the shift from 4 to 8 is performed by repeating the clutch shifting and the dog clutch shifting in the same manner as the shifting process from the first to the fourth gear, the
FIG. 4 is a graph comparing the present invention with a conventional seven-stage DCT. As shown in the figure, the overall length is reduced by about 60 mm (d), and four dog clutches have been conventionally required. Only three actuators are required and thus the actuator is also reduced.
In the conventional art, the free gear disposed on both sides of the dog clutch is constrained to the input shaft by the connection of the dog clutch to transmit the power. However, the fourth
The present invention provides an embodiment in which the double clutch transmission is applied to a hybrid vehicle in addition to the above-described double clutch transmission.
That is, as shown in FIG. 5, the hybrid vehicle is implemented not only to regenerate the hybrid vehicle but also to start the hybrid vehicle while driving.
To this end, a
The connecting
That is, the motor m is directly connected to the
At this time, when the
In addition, starting can be started when the clutch corresponding to the current running condition and the appropriate gear ratio among the
As described above, power is generated by the motor (m) during shifting of the dog clutch, thereby minimizing power transmission during shifting.
5 (b) shows that the connecting
However, in order to solve this problem, the
That is, the
When the power of the engine is charged by the motor m, charging is possible even during a stoppage. This configuration has the effect of reducing the total length of the hybrid vehicle (VW's Zeta HEV) by approximately 150 mm or more. In the case of a vehicle, it has an engine, an engine clutch, a motor, and a DCT, which is longer than the present invention by an electric length (about 90 mm) of the engine clutch and an electric field reduction amount (60 mm) of the present invention.
On the other hand, FIG. 5 (c) is a view showing a third embodiment in which the double clutch transmission according to the present invention is mounted on a hybrid vehicle and can be charged while stopped.
In order to achieve this, the present invention is characterized in that a
The structure of the double clutch transmission disclosed in FIG. 5 (b) has a disadvantage in that the
In order to compensate for this, the shaft to which the motor m is directly connected is changed from the
However, the speed of the
In the stop-charging process, all the dog clutches are released, the
While the present invention has been particularly shown and described with reference to specific embodiments thereof, it will be understood by those skilled in the art that various changes in form and details may be made therein without departing from the spirit and scope of the invention as defined by the following claims It will be apparent to those of ordinary skill in the art.
100: clutch unit 110: first clutch
120: second clutch 200: first input shaft
210: first restraining gear 220: second restraining gear
230: third restraining gear 240: first free gear
300: first synchronizer 310: second free gear
320: second dog clutch 330: third free gear
340: sixth restraining gear 350: connecting gear unit
351: restraining gear 352: seventh free gear
353: fifth dog clutch 400: second input shaft
500: second synchronizer 510: fourth free gear
520: third dog clutch 530: fifth freewheel
540: seventh restraining gear 600: third input shaft
700: fourth input shaft 710: fourth restraining gear
720: fifth restraining gear 800: drive shaft
810: drive gear 900: fifth input shaft
910: sixth freewheel gear 920: fourth dog clutch
930: rotary gear
Claims (12)
A first input shaft provided with a plurality of speed change stage drive gears and directly connected to the first clutch;
A third input shaft provided with a second input shaft and a second synchronous portion provided with a first synchronous portion that can be meshed with the plurality of speed change stage drive gears; And
And a fourth input shaft having a plurality of restraining gears arranged to engage with a part of the plurality of speed change stage drive gears so as to reduce the length of the total length, thereby performing a speed change process.
A first restraining gear, a second restraining gear, a third restraining gear, and a first free gear are rotatably inserted into the first input shaft along a longitudinal direction of the first input shaft,
The first and second restraining gears may be selectively engaged with the first and second synchronizing portions,
Wherein the third restraining gear is engaged with a part of a plurality of restraint gears provided on the fourth input shaft to perform a shifting process,
And the second clutch is directly connected to the first free gear via the hollow shaft so that the first input shaft is driven differently from the rotational speed of the engine via the second input shaft when the second clutch is engaged. Transmission.
The first clutch is directly connected to the first input shaft and is driven to have the same rotational speed as the engine at the time of engagement of the first clutch
Wherein the first input shaft and the second input shaft are selectively engaged to implement a two-stage gear ratio.
The fourth input shaft is directly connected to a fourth restraining gear and a fifth restraining gear having different sizes along the longitudinal direction of the fourth input shaft,
Wherein a gear ratio formed when the fourth restraining gear and the third restraining gear are meshed with each other and a gear ratio formed when the fifth restraining gear and the first free gear are meshed with each other are different from each other.
Wherein the first synchronization unit comprises:
A second dog clutch, and a third free gear disposed along a longitudinal direction of the second input shaft, and a sixth restraining gear is installed on one side of the second input shaft,
Wherein the second synchronizing unit comprises:
A third dog clutch and a fifth freewheel disposed at corresponding positions of the first synchronizing unit along the longitudinal direction of the third input shaft, and a third dog clutch and a fifth freewheeling gear disposed at one side of the third input shaft corresponding to the sixth constraining gear And a seventh restraining gear is provided at a position where the seventh restraining gear is disposed.
Further comprising a drive shaft provided with a drive gear,
And the sixth restraining gear and the seventh restraining gear are engaged with the driving gear to transmit power to the driving shaft.
The second and third dog clutches selectively selectively couple the second freewheel gear and the first and second free gears, or the first and second freewheeling gears, Power is transmitted to the drive shaft,
The second and third dog clutches selectively selectively engage the third freewheel gear and the second restraining gear, or the third freewheel gear and the fifth freewheel gear to selectively engage the power of the first input shaft, Is transmitted to the drive shaft,
Wherein a gear ratio of two stages is implemented by the clutch portion and a gear ratio of four stages is implemented by the first and second synchronizer portions so that a total of eight gear ratios are realized.
In order to implement the backward drive,
Further comprising a fifth input shaft provided with a sixth freewheel, a fourth dog clutch, and a rotary gear in the longitudinal direction thereof,
The sixth freewheeling gear is meshed with the third restraining gear, and the rotating gear is meshed with the seventh restraining gear.
A first input shaft provided with a plurality of speed change stage drive gears and directly connected to the first clutch;
A third input shaft provided with a second input shaft and a second synchronizing portion provided with a first synchronizing portion and a connecting gear unit that can engage with the plurality of speed change stage driving gears;
A fourth input shaft provided with a plurality of constraining gears so as to engage with a part of the plurality of speed change stage drive gears so as to reduce the length of the electric field, And
And a motor directly connected to one side of the second input shaft.
Wherein the connecting gear unit is a restraining gear, and when the first clutch and the second clutch are released, the motor is driven to enable EV traveling.
The connecting gear unit is composed of a seventh free gear and a fifth dog clutch,
The power of the motor is not transmitted to the drive shaft when the fifth dog clutch is disengaged so that the vehicle can be charged while the vehicle is stationary.
A first input shaft provided with a plurality of speed change stage drive gears and directly connected to the first clutch;
A third input shaft provided with a second input shaft and a second synchronous portion provided with a first synchronous portion that can be meshed with the plurality of speed change stage drive gears;
A fourth input shaft provided with a plurality of constraining gears so as to engage with a part of the plurality of speed change stage drive gears so as to reduce the length of the electric field, And
And a motor is directly connected to one side of the first input shaft to enable charging of the vehicle while the vehicle is stationary.
Priority Applications (1)
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KR1020140072634A KR101611047B1 (en) | 2014-06-16 | 2014-06-16 | Double clutch transmission |
Applications Claiming Priority (1)
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KR1020140072634A KR101611047B1 (en) | 2014-06-16 | 2014-06-16 | Double clutch transmission |
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Publication Number | Publication Date |
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KR20150144368A true KR20150144368A (en) | 2015-12-28 |
KR101611047B1 KR101611047B1 (en) | 2016-04-11 |
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KR1020140072634A KR101611047B1 (en) | 2014-06-16 | 2014-06-16 | Double clutch transmission |
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Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR20100064719A (en) | 2008-12-05 | 2010-06-15 | 현대자동차주식회사 | Power train of double clutch transmission |
JP2013043478A (en) | 2011-08-22 | 2013-03-04 | Honda Motor Co Ltd | Hybrid vehicle |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
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JP4193906B2 (en) * | 2007-03-26 | 2008-12-10 | 三菱自動車工業株式会社 | Double clutch transmission |
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Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR20100064719A (en) | 2008-12-05 | 2010-06-15 | 현대자동차주식회사 | Power train of double clutch transmission |
JP2013043478A (en) | 2011-08-22 | 2013-03-04 | Honda Motor Co Ltd | Hybrid vehicle |
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