JP2010276069A - Shift controller of twin clutch type transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To miniaturize a shift controller of twin clutch type transmission and simplify its structure. <P>SOLUTION: In the twin clutch type transmission, a predetermined shifting stage is established in such a way that a hydraulic pressure is supplied to first and second ports P1 and P2 arranged in each of a plurality of hydraulic actuators A1-A4 through from one side to the other side in the first and second shift valves V1 and V2, and a synchronizer is operated by the hydraulic actuators A1-A4. Furthermore, since the hydraulic actuators A1-A4 have a first inoperative mode that the hydraulic pressure does not interact on both of the first and second ports P1 and P2, and second inoperative mode that the hydraulic pressure interacts on both of the first and second ports P1 and P2, miniaturization and response characteristic can be improved by shortening the axial dimensions of the first and second shift valves V1 and V2 and hydraulic circuits can be simplified as compared with the case that the hydraulic actuators A1-A4 are kept to be inoperative with only the first inoperative mode. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a shift control device for a twin-clutch transmission that includes a plurality of meshing friction engagement elements, a first clutch that establishes an odd gear, and a second clutch that establishes an even gear.

  Such a gear shift control device for a twin clutch transmission is known from Japanese Patent Application Laid-Open No. 2004-228561.

JP 2008-309213 A

  By the way, in the twin clutch type transmission, a gear that is relatively rotatably supported on the transmission shaft is coupled to the transmission shaft using a synchromesh mechanism (meshing synchronization device) used in a manual transmission, so that a desired gear stage can be achieved. Established. A hydraulic actuator that establishes two shift stages by moving one meshing synchronizer left and right from the neutral position selectively applies hydraulic pressure to the two ports to move the piston left or right from the neutral position. And the meshing synchronizer is operated by a shift fork connected to the piston.

  For example, a multi-twin clutch transmission with seven forward speeds and one reverse speed has four hydraulic actuators that operate four meshing synchronizers, so that the operation of these hydraulic actuators can be controlled. There has been a problem in that the oil passage becomes complicated and the number of shift valves increases, and there is a problem that the valve body that accommodates the shift valve is enlarged, and the improvement has been desired.

  The present invention has been made in view of the above-described circumstances, and an object of the present invention is to reduce the size and the structure of a shift control device for a twin clutch transmission.

  To achieve the above object, according to the first aspect of the present invention, a first input shaft connected to the engine via a first clutch and a first input shaft connected to the engine via a second clutch. Two input shafts, an output shaft connected to drive wheels, a gear train for transmitting the rotation of the first and second input shafts to the output shaft, and a predetermined gear of the gear train for the first and second gears. A plurality of meshing engagement means selectively coupled to the input shaft or the output shaft, and each meshing engagement means comprising first and second ports, each of which is operated by a hydraulic pressure acting on one of the ports. A plurality of hydraulic actuators for engaging the hydraulic actuators, a hydraulic supply means for supplying hydraulic pressure to the hydraulic actuators, first and second shift valves disposed between the hydraulic actuator and the hydraulic supply means, and the first, 2nd shift valve And first and second shift valve driving means for operating the hydraulic pressure, and supplying the hydraulic pressure supplied from the hydraulic pressure supply means to the hydraulic actuator from one of the first and second shift valves via the other. In the shift control apparatus for a twin clutch transmission that operates the predetermined hydraulic actuator to establish a predetermined gear position, the hydraulic actuator has a first hydraulic pressure that does not act on both the first and second ports. A shift control device for a twin clutch transmission is proposed, which has an operation mode and a second non-operation mode in which oil pressure acts on both the first and second ports.

  According to the invention described in claim 2, in addition to the configuration of claim 1, the two hydraulic actuators have a common hydraulic pressure via a common oil passage for the two first ports. The twin clutch transmission is characterized in that four gears can be selectively established by acting different hydraulic pressures on the two second ports via separate oil passages. A transmission control device is proposed.

  The first and second output shafts 15 and 16 of the embodiment correspond to the output shaft of the present invention, and the hydraulic pump 41 of the embodiment corresponds to the hydraulic pressure supply means of the present invention. The fourth hydraulic actuators A1 to A4 correspond to the hydraulic actuator of the present invention, the odd-numbered clutch C1 of the embodiment corresponds to the first clutch of the present invention, and the even-numbered clutch C2 of the embodiment corresponds to the first of the present invention. Corresponding to two clutches, the first to fourth synchronizers S1 to S4 of the embodiment correspond to the meshing engagement means of the present invention, and the first and second on / off solenoids SA and SB respectively correspond to the present invention. This corresponds to the first and second shift valve driving means.

  According to the configuration of the first aspect, in the twin clutch transmission, the hydraulic pressure supplied from the hydraulic pressure supply means is provided to each of the plurality of hydraulic actuators from one of the first and second shift valves via the other. 1. Supply to the first and second ports, and establish a predetermined gear position by operating the synchronization device with a hydraulic actuator. The hydraulic actuator has a first inoperative mode in which hydraulic pressure does not act on both the first and second ports, and a second inoperative mode in which hydraulic pressure acts on both the first and second ports. Compared to maintaining the hydraulic actuator in an inoperative state only in the first inoperative mode, the axial dimensions of the first and second shift valves are shortened to reduce the size and improve the response and simplify the hydraulic circuit. Can be achieved.

  According to the configuration of claim 2, the common hydraulic pressure is applied to the two first ports of the two hydraulic actuators via the common oil passage, and the two second ports of the two hydraulic actuators are applied. Since different hydraulic pressures are applied via the separate oil passages, one of the hydraulic actuators can be operated at two positions and the other hydraulic actuator can be operated at two positions to establish four shift stages.

Skeleton diagram of twin clutch transmission. The figure which shows the hydraulic circuit which controls a hydraulic actuator. Operation table of on / off solenoid and shift valve for each gear position. The figure which shows the hydraulic circuit at the time of establishment of a reverse gear stage and a 1-speed gear stage. The figure which shows the hydraulic circuit at the time of establishment of the 2nd gear stage and the 3rd gear stage. The figure which shows the hydraulic circuit at the time of establishment of the 4th gear stage and the 5th gear stage. The figure which shows the hydraulic circuit at the time of establishment of 6th speed gear stage and 7th speed gear stage. The figure which shows the operating principle of a hydraulic actuator. The figure which shows the action | operation concept of a hydraulic actuator and a shift valve.

  Hereinafter, embodiments of the present invention will be described with reference to FIGS.

  As shown in FIG. 1, a twin clutch transmission T having 7 forward speeds and 1 reverse speed includes an odd-numbered clutch C1 and an even-numbered clutch C2 that are coaxially connected to a crankshaft 11 of an engine E via a damper 12. A first input shaft 13 and a second input shaft 14 that are coaxial with the crankshaft 11 and arranged radially inside and outside of the crankshaft 11; a first output shaft 15 that is arranged in parallel with the first and second input shafts 13 and 14; A second output shaft 16. When the odd-numbered clutch C1 is engaged, the crankshaft 11 is coupled to the first input shaft 13, and when the even-numbered clutch C2 is engaged, the crankshaft 11 is coupled to the second input shaft 14.

  A first speed drive gear 17, a third speed drive gear 18, a fifth speed drive gear 19 and a seventh speed drive gear 20 are fixed to the first input shaft 13 on the radially inner side, and the second input shaft 14 on the radially outer side is fixed to the first input shaft 13. A 2nd speed-reverse drive gear 21 and a 4th speed-6th speed drive gear 22 are fixed.

  The first output shaft 15 includes a first speed driven gear 23 that meshes with the first speed drive gear 17, a second speed driven gear 24 that meshes with the second speed-reverse drive gear 21, and a third speed driven gear 25 that meshes with the third speed drive gear 18. A 4-speed driven gear 26 meshing with the 4-speed-6-speed drive gear 22 is supported so as to be relatively rotatable. The first speed driven gear 23 and the third speed driven gear 25 can be selectively coupled to the first output shaft 15 by the first synchronizer S1, and the second speed driven gear 24 and the fourth speed driven gear 26 are the first output shaft by the second synchronizer S2. 15 can be selectively combined.

  The second output shaft 16 has a 5-speed driven gear 27 meshed with the 5-speed drive gear 19, a 6-speed driven gear 28 meshed with the 4-speed-6-speed drive gear 22, and a 7-speed driven gear 29 meshed with the 7-speed drive gear 20. And a reverse driven gear 31 that meshes with the second speed-reverse drive gear 21 via a reverse idle gear 30 is supported in a relatively rotatable manner. The fifth speed driven gear 27 and the seventh speed driven gear 29 can be selectively coupled to the second output shaft 16 by the third synchronizer S3. The sixth speed driven gear 28 and the reverse driven gear 31 can be selectively coupled to the second output shaft 16 by the fourth synchronizer S4. Can be selectively combined.

  The first final drive gear 32 fixed to the first output shaft 15 and the second final drive gear 33 fixed to the second output shaft 16 mesh with the final driven gear 34 of the differential gear D.

  Thus, when the odd-numbered clutch C1 is engaged with the first synchronizer S1 moved to the right and the first-speed driven gear 23 is coupled to the first output shaft 15, the first gear is established, and the second synchronizer S2 is When the even speed clutch C2 is engaged with the second speed driven gear 24 coupled to the first output shaft 15 with the second speed driven to the left, the second speed gear stage is established, and the first synchronizer S1 is moved to the left to move the third speed driven gear 25. When the odd-numbered clutch C1 is engaged with the first output shaft 15 being engaged, the third speed is established, and the second synchronizer S2 is moved to the right to connect the fourth speed driven gear 26 to the first output shaft 15. When the even-numbered clutch C2 is engaged, the second gear is established.

  Further, when the third synchronizer S3 is moved to the right and the odd speed clutch C1 is engaged with the fifth speed driven gear 27 coupled to the second output shaft 16, the fifth gear is established, and the fourth synchronizer S4 is moved to the right. When the even-speed clutch C2 is engaged with the 6-speed driven gear 28 coupled to the second output shaft 16, the 6-speed gear stage is established, and the third synchronizer S3 is moved to the left to move the 7-speed driven gear 29 to the second speed. When the odd-numbered clutch C1 is engaged with the output shaft 16 connected, the seventh gear is established, and the fourth synchronizer S4 is moved to the left to connect the reverse driven gear 31 to the second output shaft 16 and the even-numbered gear. When the clutch C2 is engaged, a reverse gear position is established.

  FIG. 2 is a hydraulic circuit that drives the first to fourth hydraulic actuators A1 to A4 that operate the first to fourth synchronization devices S1 to S4. 2, the first to fourth hydraulic actuators A1 to A4 include first ports P1... At the right end and second ports P2... At the left end, and the first and second ports P1 and P2. It is driven from the neutral position to the left and right positions by the pressure difference of the hydraulic pressure acting on. At this time, separate hydraulic pressures are supplied to the two first ports P1 and P1 of the first and third hydraulic actuators A1 and A3 involved in the establishment of the odd-numbered shift stage, and the two second ports P2 and P2 are supplied. Are supplied with a common hydraulic pressure. Similarly, the two first ports P1 and P1 of the second and fourth hydraulic actuators A2 and A4 involved in the establishment of the even-numbered gear stage (including the reverse gear stage) are separately provided. The common hydraulic pressure is supplied to the two second ports P2 and P2.

  When the first to fourth hydraulic actuators A1 to A4 are moved left or right from the neutral position, the first to fourth synchronization devices S1 to S4 are moved from the neutral position to the left or right by a fork (not shown) provided thereon. And the corresponding gear is established.

  The first hydraulic actuator A1 establishes the first speed shift stage when the hydraulic pressure acts on the second port P2 and moves to the right, and conversely shifts the third speed when the hydraulic pressure acts on the first port P1 and moves left. A stage is established. The second hydraulic actuator A2 establishes a second speed shift stage by moving to the right with hydraulic pressure acting on the second port P2, and conversely shifting to the fourth speed by moving to the left with hydraulic pressure acting on the first port P1. A stage is established. The third hydraulic actuator A3 establishes the seventh speed shift stage when the hydraulic pressure acts on the second port P2 and moves to the right, and conversely the fifth pressure shifts when the hydraulic pressure acts on the first port P1 and moves left. A stage is established. The fourth hydraulic actuator A4 establishes a reverse gear position when the hydraulic pressure acts on the second port P2 and moves to the right, and on the contrary, the hydraulic pressure acts on the first port P1 and moves to the left to cause the sixth speed gear stage. Established.

  The hydraulic pressure generated by the hydraulic pump 41 is regulated by the regulator valve 42 to become line pressure, and the excess oil in the regulator valve 42 is partly lubricated via the relief valve 43 to lubricate the transmission T. .

  The third shift valve V3, which is supplied with line pressure via the third on / off solenoid valve SC and can be switched between two positions, has a control pressure obtained by adjusting the line pressure with the first linear solenoid valve LA, This is selectively supplied to the second shift valves V1, V2 and the even-numbered clutch C2 that establishes the even-numbered gear (including the reverse gear). The fourth shift valve V4, which is supplied with the line pressure via the fourth on / off solenoid valve SD and can switch between the two positions, has a control pressure obtained by adjusting the line pressure with the second linear solenoid valve LB. The second shift valves V1 and V2 and the odd-numbered clutch C1 that establishes the odd-numbered gear are selectively supplied.

  The first shift valve V1 is supplied with line pressure via a first on / off solenoid valve SA and can be switched between two positions. The second shift valve V2 is switched via a second on / off solenoid valve SB. Line pressure is supplied and the two positions can be switched.

  When the fourth on / off solenoid valve SD is turned on and the spool of the fourth shift valve V4 is moved to the right, one of the odd-numbered gears is preliminarily established (pre-shifted), and in this state, the fourth on / off solenoid is operated. When the valve SD is turned OFF and the spool of the fourth shift valve V4 moves to the left, the odd-numbered clutch C1 is engaged and any of the odd-numbered gears is established. In the state where the third on / off solenoid valve SC is turned ON and the spool of the third shift valve V3 is moved to the right when the odd speed is established, any of the even speed is pre-established (pre-shifted). In this state, when the third on / off solenoid valve SC is turned OFF and the spool of the third shift valve V3 is moved to the left, the even-numbered clutch C2 is engaged and any of the even-numbered gears is established.

  Thus, by alternately turning on / off the third on / off solenoid valve SC and the fourth on / off solenoid valve SD, it is possible to shift up or down while preventing the driving force from being lost.

  Next, the operation of the first hydraulic actuator A1 to the fourth hydraulic actuator A4 will be described.

  As shown in FIG. 3, the pre-shift mode includes a 1-speed-reverse mode, a 2-speed-3 speed mode, a 4-speed-5-speed mode, and a 6-speed-7-speed mode. In the mode, the first on / off solenoid valve SA is turned off and the second on / off solenoid valve SB is turned on (see FIG. 4). In the second speed / third speed mode, the first on / off solenoid valve SA is turned off. The second on / off solenoid valve SB is turned off (see FIG. 5). In the 4th-5th speed mode, the first on / off solenoid valve SA is turned on and the second on / off solenoid valve SB is turned off (FIG. 6). In the 6th to 7th speed mode, the first on / off solenoid valve SA is turned on and the second on / off solenoid valve SB is turned on (see FIG. 7).

  As shown in FIG. 4A, in the first speed-reverse mode in which the first on / off solenoid valve SA is turned off and the second on / off solenoid valve SB is turned on, the first linear solenoid valve LA is turned on. The reverse gear is established by the hydraulic pressure acting on the second port P2 of the four hydraulic actuator A4 and the fourth synchronizer S4 operating. At this time, the hydraulic pressure also acts on the first and second ports P1 and P2 of the second hydraulic actuator A2, but the second hydraulic actuator A2 does not operate because these hydraulic pressures are opposed at the same pressure.

  As shown in FIG. 4B, in the first speed-reverse mode in which the first on / off solenoid valve SA is turned off and the second on / off solenoid valve SB is turned on, the second linear solenoid valve LB is turned on. The first gear is established by the hydraulic pressure acting on the second port P2 of the first hydraulic actuator A1 and the first synchronizer S1 operating. At this time, the hydraulic pressure also acts on the first and second ports P1, P2 of the third hydraulic actuator A3, but the third hydraulic actuator A3 does not operate because the hydraulic pressures are opposed to each other at the same pressure.

  As shown in FIG. 5 (A), when the first linear solenoid valve LA is turned on in the 2nd-3rd speed mode in which both the first on / off solenoid valve SA and the second on / off solenoid valve SB are turned off, the second The second speed gear stage is established by the hydraulic pressure acting on the second port P2 of the hydraulic actuator A2 to operate the second synchronization device S2. At this time, the hydraulic pressure also acts on the first and second ports P1 and P2 of the fourth hydraulic actuator A4, but since the hydraulic pressures face each other at the same pressure, the fourth hydraulic actuator A4 does not operate.

  As shown in FIG. 5B, when the second linear solenoid valve LB is turned on in the second speed-third speed mode in which both the first on / off solenoid valve SA and the second on / off solenoid valve SB are turned off, the first The third gear is established by the hydraulic pressure acting on the first port P1 of the hydraulic actuator A1 to operate the first synchronizer S1.

  As shown in FIG. 6A, when the first linear solenoid valve LA is turned on in the 4-speed-5-speed mode in which the first on / off solenoid valve SA is turned on and the second on / off solenoid valve SB is turned off. The oil pressure acts on the first port P1 of the second hydraulic actuator A2 and the second synchronizer S2 operates to establish the fourth gear.

  As shown in FIG. 6B, when the second linear solenoid valve LB is turned on in the 4th-5th speed mode in which the first on / off solenoid valve SA is turned on and the second on / off solenoid valve SB is turned off. The fifth gear is established by the hydraulic pressure acting on the first port P1 of the third hydraulic actuator A3 to operate the third synchronizer S3.

  As shown in FIG. 7A, when the first linear solenoid valve LA is turned on in the 6th to 7th speed mode in which both the first on / off solenoid valve SA and the second on / off solenoid valve SB are turned on, the fourth state is reached. The sixth speed is established by the hydraulic pressure acting on the first port P1 of the hydraulic actuator A4 to operate the fourth synchronizer S4.

  As shown in FIG. 7B, when the second linear solenoid valve LB is turned on in the 6th to 7th speed mode in which both the first on / off solenoid valve SA and the second on / off solenoid valve SB are turned on, the third The seventh gear is established by the hydraulic pressure acting on the second port P2 of the hydraulic actuator A3 to operate the third synchronizer S3. At this time, the hydraulic pressure also acts on the first and second ports P1, P2 of the first hydraulic actuator A1, but the first hydraulic actuator A1 does not operate because the hydraulic pressures are opposed to each other at the same pressure.

  Conventionally, when the hydraulic actuator is not operated, the hydraulic pressure is not applied to both ends of the piston of the hydraulic actuator, but in this embodiment, the first inoperative mode in which the hydraulic pressure is not applied to both ends of the piston of the hydraulic actuator, and the hydraulic actuator The second non-operation mode in which the same hydraulic pressure is applied to both ends of the piston is used in combination, so that the axial dimensions of the first and second shift valves V1, V2 are reduced and the oil passage is simplified. Yes. Hereinafter, the reason why the axial dimensions of the first and second shift valves V1, V2 can be reduced and the oil passage can be simplified will be described.

  Since the first and third hydraulic actuators A1 and A3 on the right side and the second and fourth hydraulic actuators A2 and A4 on the left side in FIG. 2 have substantially the same symmetrical structure, the first and third hydraulic actuators A1 and A3 will be described as an example.

  As shown in FIG. 8 as a conventional example, the hydraulic pressure applied to the second port P2 of the first hydraulic actuator A1 is B, the hydraulic pressure applied to the first port P1 is D, and the hydraulic pressure applied to the second port P2 of the third hydraulic actuator A3. Is A, and the hydraulic pressure applied to the first port P1 is C. When the hydraulic pressure A is applied, the third hydraulic actuator A3 moves to the right, when the hydraulic pressure B is applied, the first hydraulic actuator A1 moves to the right, and when the hydraulic pressure C is applied, the third hydraulic actuator A3 moves to the left, and the hydraulic pressure D As a result, the first hydraulic actuator A1 moves to the left. That is, conventionally, the operation of the first hydraulic actuator A1 and the third hydraulic actuator A3 is controlled in four modes by controlling four types of hydraulic pressures A, B, C, and D.

  On the other hand, in the embodiment of FIG. 8, as shown in the left column, when the hydraulic pressure C is applied, the third hydraulic actuator A3 moves to the left, and when the hydraulic pressure D is applied, the first hydraulic actuator A1 moves to the left. To do. So far, it is the same as the conventional example. However, when the hydraulic pressures A, B, and D are applied, the hydraulic pressures B and D cancel each other, the first hydraulic actuator A1 does not operate, and the third hydraulic actuator A3 moves to the right. When the hydraulic pressures A, B, and C are applied, the hydraulic pressures A and C cancel each other, the third hydraulic actuator A3 does not operate, and the first hydraulic actuator A1 moves to the right. At this time, since the hydraulic pressures A and B are turned on / off in exactly the same manner, they can be collectively controlled as the hydraulic pressure A without separately controlling them.

  That is, as shown in the right column of the embodiment of FIG. 8, the second ports P2 and P2 of the first hydraulic actuator A1 and the third hydraulic actuator A3 perform ON / OFF control of the same hydraulic pressure A, so that FIG. As in the left column of the embodiment, the first hydraulic actuator A1 and the third hydraulic actuator A3 can be moved right and left, respectively, to exhibit the same function as the conventional example.

  FIG. 9 is a diagram schematically showing the conventional example and the embodiment shown in FIG. Shift valves VA, VB, and VC schematically show the functions of the first shift valve V1 and the second shift valve V2 of the embodiment, and in the conventional example of FIG. 9A, the first hydraulic actuator A1 and the first shift valve V1 are shown. Since the different hydraulic pressures A and B are supplied to the second ports P2 and P2 of the three hydraulic actuator A3, the shift valves VB and VC cannot be reduced in size. On the other hand, in the embodiment of FIG. 9B, the shift valves VB and VC are downsized to supply the same hydraulic pressure A to the second ports P2 and P2 of the first hydraulic actuator A1 and the third hydraulic actuator A3. Is possible.

  As described above, according to the present embodiment, in the twin clutch transmission T, the first to fourth hydraulic actuators for establishing the desired shift stage by operating the first to fourth synchronization devices S1 to S4. A first inoperative mode in which the hydraulic pressure does not act on both the first and second ports P1 and P2 when the hydraulic pressure is applied to the first and second ports P1 and P2 provided in each of A1 to A4; Since the second non-operation mode in which the hydraulic pressure acts on both the first and second ports P1 and P2 is used in combination, the first to fourth hydraulic actuators A1 to A4 are in the non-operation state only in the first non-operation mode. Compared with the case of maintaining the above, the axial dimensions of the first and second shift valves V1, V2 can be shortened to reduce the size and improve the responsiveness and simplify the hydraulic circuit.

  In particular, the two hydraulic actuators (the first and third hydraulic actuators A1 and A3 or the second and fourth hydraulic actuators A2 and A4) have a common oil path common to the two second ports P2 and P2. Since hydraulic pressure is applied and different hydraulic pressures are applied to the two first ports P1 and P1 via separate oil passages, one hydraulic actuator is operated to the 2 position and the other hydraulic actuator is set to the 2 position. It can be activated to establish four gear stages.

  The embodiments of the present invention have been described above, but various design changes can be made without departing from the scope of the present invention.

  For example, the transmission T according to the embodiment includes the first to fourth actuators A1 to A4. However, the present invention is valid if it has two hydraulic actuators.

  The structure of the transmission T is not limited to that of the embodiment, and may be a twin clutch type.

13 First input shaft 14 Second input shaft 15 First output shaft (output shaft)
16 Second output shaft (output shaft)
41 Hydraulic pump (hydraulic supply means)
A1 1st hydraulic actuator (hydraulic actuator)
A2 Second hydraulic actuator (hydraulic actuator)
A3 Third hydraulic actuator (hydraulic actuator)
A4 4th hydraulic actuator (hydraulic actuator)
C1 odd-numbered clutch (first clutch)
C2 Even-numbered clutch (second clutch)
E engine P1 first port P2 second port S1 first synchronizer (meshing engagement means)
S2 Second synchronizer (meshing engagement means)
S3 Third synchronizer (meshing engagement means)
S4 Fourth synchronization device (meshing engagement means)
SA First on / off solenoid valve (first shift valve drive means)
SB Second on / off solenoid valve (second shift valve drive means)
V1 1st shift valve V2 2nd shift valve

Claims (2)

A first input shaft (13) connected to the engine (E) via a first clutch (C1);
A second input shaft (14) connected to the engine (E) via a second clutch (C2);
Output shafts (15, 16) connected to the drive wheels;
A gear train for transmitting the rotation of the first and second input shafts (13, 14) to the output shaft (15, 16);
A plurality of meshing engagement means (S1 to S4) for selectively coupling a predetermined gear of the gear train to the first and second input shafts (13, 14) or the output shaft (15, 16);
Each of the plurality of first and second ports (P1, P2) is operated by hydraulic pressure acting on one of the ports (P1, P2) to engage the meshing engagement means (S1 to S4). Hydraulic actuators (A1 to A4);
Hydraulic pressure supply means (41) for supplying hydraulic pressure to the hydraulic actuators (A1 to A4);
First and second shift valves (V1, V2) disposed between the hydraulic actuators (A1 to A4) and the hydraulic pressure supply means (41);
First and second shift valve driving means (SA, SB) for operating the first and second shift valves (V1, V2), respectively.
By supplying the hydraulic pressure supplied from the hydraulic pressure supply means (41) from one of the first and second shift valves (V1, V2) to the hydraulic actuator (A1 to A4) via the other, a predetermined amount is obtained. In the shift control device for a twin clutch transmission that operates the hydraulic actuators (A1 to A4) to establish a predetermined shift speed,
The hydraulic actuators (A1 to A4) include both a first inoperative mode in which hydraulic pressure does not act on both the first and second ports (P1, P2), and both the first and second ports (P1, P2). And a second non-operational mode in which hydraulic pressure acts on the transmission control device for the twin clutch transmission.   In the two hydraulic actuators (A1, A3; A2, A4), a common hydraulic pressure acts on the two first ports (P1) through a common oil passage, and the two second actuators (A1, A3; A2, A4). 4. The twin clutch transmission according to claim 1, wherein four gears can be selectively established by applying different hydraulic pressures to the port (P2) via different oil passages. Shift control device.

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