JP2007032620A - Twin clutch type transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a twin clutch type transmission which can materialize miniaturization and reduce inertia of an input shaft. <P>SOLUTION: A twin clutch type transmission is equipped with a first input shaft 2 in which power of an internal combustion engine is input through the medium of a first clutch C1, a second input shaft 3 externally fitted coaxially with the first input shaft 2 in which power of an internal combustion engine is input through the medium of a second clutch C2, and gear mechanism for transmitting to an output shaft 5 the power which is input to the second input shaft 3 through the medium of a first transmission ratio. The gear mechanism is equipped with a play gear G6 fitted loose into the first input shaft 2, a fixed gear G6' fixed and arranged in a counter shaft 4 always meshed with the play gear G6 and a synchronizer S6 fixed and arranged in the second input shaft 3 for integrally rotating the play gear G6 and the second input shaft 3 by selecting the play gear G6. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a twin clutch type transmission.

Conventionally, as this type of transmission, for example, as disclosed in Patent Document 1, a first input shaft connected to an engine via a first clutch and a first input shaft connected to the engine via a second clutch are disclosed. A second input shaft that is coaxially disposed outside one input shaft, a plurality of drive gears disposed on the first input shaft and the second input shaft, and a driven gear that meshes with the plurality of drive gears are disposed. An output shaft has been proposed.
In this transmission, by changing the first clutch and the second clutch, the power from the engine can be shifted to a desired gear ratio and output.
JP 2004-28117 A

However, since such a transmission has a structure in which the drive gear on the second input shaft is arranged as an idler gear, the inner diameter of the gear on the second input shaft formed on the hollow shaft is large. In addition to this, the inner diameter of the gear must be further increased in order to obtain a free-wheeling gear, and as a result, the synchro diameter of the synchronizing device for selecting the free-wheeling gear may increase.
In order to solve this, the drive gear on the second input shaft may be a fixed gear, and the driven gear on the output shaft meshing therewith may be an idler gear. Since the gear diameter is relatively small, it is difficult to configure it as an idler gear.

  The present invention has been devised in view of the above-described conventional problems, and is intended to reduce the size of the transmission and to reduce the inertia of the shaft. Item 1 is coaxially fitted to the first input shaft to which the power of the internal combustion engine is input via the first clutch and the first input shaft to which the power of the internal combustion engine is input via the second clutch. A twin clutch type transmission comprising: a second input shaft; and a gear mechanism that transmits the power input to the second input shaft to the output shaft with a first speed ratio. An idle gear that is loosely fitted to the first input shaft, a fixed gear that is fixedly arranged on the output shaft that is always meshed with the idle gear, and the idle gear that selects the idle gear and the second gear Selection means fixedly arranged on the second input shaft for integrally rotating the input shaft; It is be provided.

According to a second aspect of the present invention, the idle gear is formed with a larger number of teeth than the fixed gear so as to increase the rotational speed of the second input shaft and transmit it to the output shaft as the predetermined gear ratio. It is to become.
Further, a third aspect of the present invention is the twin clutch transmission according to the first or second aspect, wherein the idle gear has a sixth speed that is a sixth speed. It is to be.
According to a fourth aspect of the present invention, the selecting means rotates the idle gear and the second input shaft integrally while synchronizing the rotational speed of the idle gear with the rotational speed of the second input shaft. It is to be.

  The twin clutch type transmission of the present invention is coaxial with a first input shaft to which the power of the internal combustion engine is input via the first clutch and a first input shaft to which the power of the internal combustion engine is input via the second clutch. And a gear mechanism for transmitting the power input to the second input shaft to the output shaft with a first gear ratio, and the gear mechanism is free to play on the first input shaft. A fitted idle gear, a fixed gear fixed to an output shaft that is always meshed with the idle gear, and a second gear that selects the idle gear and rotates the idle gear and the second input shaft together. And a selection means fixedly disposed on the input shaft, thereby providing a loosely-fitted free fit on the first input shaft as a gear mechanism for transmitting the power input to the second input shaft to the output shaft with a first speed ratio. A rotating gear, a fixed gear fixedly disposed on an output shaft that is always meshed with the rotating gear, Since there is a selection shaft fixedly arranged on the second input shaft for integrally rotating the idle gear and the second input shaft by selecting the gear, it is not necessary to increase the inner diameter of the idle gear, so that the selection means Of the input shaft can be suppressed, and as a result, the inertia of the input shaft can be reduced.

  In addition, the idler gear has a larger number of teeth than the fixed gear so as to increase the rotation speed of the second input shaft as a predetermined gear ratio and transmit it to the output shaft, thereby increasing the size of the selection means. Can be more effectively suppressed.

  Further, the idle gear is a gear that constitutes the sixth speed gear stage, so that it is possible to effectively prevent the selection means from becoming large in a transmission having six forward speed gear stages. Become.

  The selection means is means for rotating the idle gear and the second input shaft integrally while synchronizing the rotation speed of the idle gear with the rotation speed of the second input shaft. It can be rotated integrally with the second input shaft while being synchronized with the two input shafts.

Embodiments of the present invention will be described below with reference to the drawings.
FIG. 1 is a schematic configuration diagram of a twin clutch transmission having six forward speeds.
As shown in the figure, the twin clutch type transmission 1 of the embodiment includes a first input shaft 2 to which power from the engine is selectively input via a clutch C1 connected to the crankshaft CS of the engine, and the engine. The second input shaft 3 to which power from the engine is selectively input via the clutch C2 connected to the crankshaft CS of the first input shaft 2 and the power input to the first input shaft 2 and the second input shaft 3 are shifted. The transmission mechanism TM that outputs to the output shaft 5 and the transmission case 8 that accommodates them are provided.

  The first input shaft 2 has a front end portion close to the clutches C1 and C2 that is coaxially fitted to the second input shaft 3 and is rotatably supported by the second input shaft 3 by needle bearings 7 and 7 '. 2 A rear end protruding from the input shaft 3 is rotatably supported by an intermediate wall 8b of the transmission case 8 via a ball bearing 6 ', and is rearward of the transmission case 8 via a ball bearing 6' '. The output shaft 5 rotatably supported on the wall 8c is supported by a needle bearing 7 '' so as to be rotatable. Further, the second input shaft 3 is formed as a hollow shaft whose front end portion close to the clutches C1 and C2 is rotatably supported on the front wall 8a of the transmission case 8 via the ball bearing 6.

  The speed change mechanism TM includes a drive gear G carried on the first input shaft 2 and the second input shaft 3, a driven gear G ′ carried on the counter shaft 4 meshing with the drive gear G, and the first input shaft 2. And a synchronizing device S fixedly supported on the second input shaft 3 and the counter shaft 4, and a synchronous mesh type that performs a shifting action using the driving gear G, the driven gear G ′, and the synchronizing device S as transmission elements. It is configured as a transmission mechanism. In the embodiment, the driving gear G and the driven gear G ′ are configured by the sixth forward speed and the reverse speed.

  Among the drive gears G, the first speed drive gear G1 and the reverse drive gear GR are fixedly supported on the first input shaft 2, and the third speed drive gear G3 and the sixth speed drive gear G6 are the first input shaft. 2 and 1st-speed driven gear G1 'meshing with 1st-speed driving gear G1 and reverse driven gear GR' meshing with reverse driving gear GR. The counter shaft 4 is rotatably supported by a counter gear and a third speed driven gear G3 ′ meshed with the third speed drive gear G3 and a sixth speed driven gear G6 ′ meshed with the sixth speed drive gear G6 are counters. The shaft 4 is fixedly supported.

The first input shaft 2 includes an output gear (for the fifth speed) in which the third and fifth speed synchronizer S35 of the synchronizer S is fixedly supported at the foremost end of the third speed drive gear G3 and the output shaft 5. The 1 / reverse synchronizer S1R is fixedly supported between the first-speed driven gear G1 ′ and the reverse driven gear GR ′ of the countershaft 4 between the gear and the gear GO. The arrangement of the first speed drive gear G1, the reverse drive gear GR, the third speed drive gear G3, the sixth speed drive gear G6 and the third and fifth speed synchronizer S35 on the first input shaft 2 in the embodiment is as follows. A 6-speed drive gear G6 is disposed at the forefront adjacent to the 6-speed synchronizer S6, and the first-speed drive gear G1, reverse drive gear GR, third-speed drive gear G3, 3,. It is arranged with a 5-speed synchronizer S35.
A ball bearing 6 'is disposed between the reverse drive gear GR and the third speed drive gear G3, and the first speed drive gear G1 and the reverse drive gear that transmit a relatively large torque output. Each of the GR and the third speed drive gear G3 is configured to be disposed in the vicinity of the ball bearing 6 ′.

An output counter gear GC meshing with the output gear (5-speed gear) GO is fixedly supported on the counter shaft 4.
Further, among the drive gears G, the second-speed drive gear G2 and the fourth-speed drive gear G4 are fixedly supported on the second input shaft 3, and among the driven gears G ′, the second-speed drive gear G2 and A counter gear 4 is rotatably supported by a counter shaft 4 that is engaged with a second speed driven gear G2 ′ and a fourth speed driven gear G4.
Among the synchronizers S, the 6-speed synchronizer S6 is the second input shaft 3, and the 2-4 speed synchronizer S24 is the 2-speed driven gear G2 'and the 4-speed driven gear G4 of the counter shaft 4. 'Is fixedly supported between.
The arrangement of the second-speed drive gear G2, the fourth-speed drive gear G4 and the sixth-speed synchronizer S6 on the second input shaft 3 transmits a larger torque output than the fourth-speed drive gear G4 in the embodiment. The second-speed drive gear G2 and the fourth-speed drive gear G4 are arranged in this order so that the second-speed drive gear G2 is in the vicinity of the ball bearing 6, and the sixth-speed synchronizer S6 is arranged at the rearmost end.

  Therefore, the power from the engine is generated by selecting the first-speed drive gear G1 ′ or the reverse drive gear GR ′ that idles on the countershaft 4 by the 1 / reverse synchronizer S1R fixedly supported on the countershaft 4. The first input shaft 2 can shift to the first speed or reverse and output to the output shaft 5, and idles on the first input shaft 2 by the third and fifth speed synchronizer S35 fixedly supported on the first input shaft 2. By selecting the third speed drive gear G3 or the output gear (fifth gear) GO fixed on the output shaft 5, the power from the engine is shifted from the first input shaft 2 to the third speed or the fifth speed and output. The second-speed driven gear G2 ′ or the fourth-speed driven gear G4 ′ that can rotate on the countershaft 4 by the second and fourth-speed synchronization device S24 fixedly supported on the countershaft 4 can be selected. From the engine The power can be shifted from the second input shaft 3 to the second speed or the fourth speed and output to the output shaft 5. Further, the 6-speed synchronizer S 6 fixedly supported on the second input shaft 3 moves the first input shaft 2. By selecting the 6-speed drive gear G6 that rotates freely, the power from the engine can be shifted from the second input shaft 3 to the 6th speed and output to the output shaft 5.

  That is, the power input from the engine to the first input shaft 2 is shifted to the first, third, and fifth odd-numbered or reverse gears, and the first, third, and reverse gears are the output counter gear GC and the output gear. (Fifth speed gear) Output to the output shaft 5 via GO, and the fifth speed is directly output from the first input shaft 2 to the output shaft 5. Further, the power input from the engine to the second input shaft 3 is shifted to even gears of 2nd speed, 4th speed, and 6th speed, and output through the output counter gear GC and the output gear (5th speed gear) GO. It is output to the shaft 5.

Here, the sixth-speed drive gear G6, which is the sixth-speed drive gear G achieved through the second input shaft 3, is rotated on the first input shaft 2 instead of on the second input shaft 3, Since the 6-speed synchronizer S6 fixedly supported on the two input shafts 3 is selected, the idle gear is not disposed on the second input shaft 3 formed as a hollow shaft, and the minimum gear diameter is set. The 6th speed stage can be achieved without forming the 6th speed driven gear G6 ′ as a free-wheeling gear. As a result, an increase in the size of the 6-speed synchronization device S6 can be suppressed, so that the inertia of the second input shaft 3 can be reduced and the transmission itself can be downsized.
Further, as described above, by adopting a structure in which adjacent shift speeds can be achieved by different input shafts, a so-called pre-shift state in which the next shift speed to be selected can be selected in advance can be achieved. That is, during traveling at the first speed, the second-speed drive gear G2 can be selected in advance by the second- and fourth-speed synchronization device S24. If it carries out like this, it can shift smoothly only by changing clutch C1 and C2. Of course, it is possible to shift without entering the pre-shift state.

Next, the operation of the thus configured twin clutch transmission, particularly the operation when shifting to the sixth speed will be described.
Consider a case where there is a shift request to 6th speed while traveling at 5th speed. During traveling at the fifth speed, the clutch C1 is connected to the crankshaft CS, and the third and fifth speed synchronizer S35 selects the output gear (fifth speed gear) GO. The input power is transmitted to the output shaft 5 in a directly connected state, and the clutch C2 is disconnected from the crankshaft CS and the 6-speed synchronizer S6 preselects the 6-speed drive gear G6. Pre-shift state. At this time, the 6-speed drive gear G6 receives the rotation of the first input shaft 2 via the output counter gear GC and the 6-speed driven gear G6 ′ and rotates relative to the first input shaft 2. Yes. That is, the second input shaft 3 is rotated relative to the first input shaft 2 at the sixth speed by the sixth speed drive gear G6. From such a state, the shift from the fifth speed to the sixth speed is completed by releasing the connection between the clutch C1 and the crankshaft CS and connecting the clutch C2 and the crankshaft CS.
In this way, the sixth-speed drive gear G6, which is the sixth-speed drive gear G achieved through the second input shaft 3, is idled on the first input shaft 2, not on the second input shaft 3. Thus, an increase in the size of the 6-speed synchronizer S6 can be suppressed, a pre-shift state can be achieved, and a smooth shift can be achieved simply by switching the clutches C1 and C2.

  According to the twin clutch transmission 1 of the embodiment described above, the 6-speed synchronization device S6 is fixedly supported on the second input shaft 3, and the 6-speed drive gear G6 can be rotated on the first input shaft 2. The 6th speed driving gear G6 is selected by the 6th speed synchronizer S6, and the power input from the engine to the second input shaft 3 is shifted to the 6th speed and output to the output shaft 5 Therefore, the idle gear is not disposed on the second input shaft 3 formed as a hollow shaft, and the 6-speed driven gear G6 ′ having the minimum gear diameter is not formed as an idle gear. High speed can be achieved. As a result, an increase in the size of the 6-speed synchronization device S6 can be suppressed, so that the inertia of the second input shaft 3 can be reduced and the transmission itself can be downsized.

  In the twin clutch transmission 1 of the embodiment, the power input from the engine by the first input shaft 2 is shifted to an odd speed and output to the output shaft 5, and the power input from the engine by the second input shaft 3. Is shifted to an even gear and output to the output shaft 5. Conversely, for example, the first input shaft 2 shifts the power input from the engine to the first speed, the second speed, and the third speed. The first input shaft 2 and the second input, such as those that output to the output shaft 5 and the second input shaft 3 shifts the power input from the engine to the 4th speed, 5th speed, 6th speed and outputs to the output shaft 5 The shaft 3 may shift the power input from the engine to any gear stage. In this case, the synchronization device S fixedly supported on the second input shaft 3 and the drive gear G rotatably supported on the first input shaft 2 are not limited to the 6-speed synchronization device S6 and the 6-speed drive gear G6. The 4-speed synchronizer S4 and the 4-speed drive gear G4, the 5-speed synchronizer S5, and the 5-speed drive gear G5, etc. may be used.

  The twin clutch transmission 1 of the embodiment is a twin clutch transmission having six forward speeds, but may have any speed such as four forward speeds, five speeds, and seven speeds.

  In the twin-clutch transmission 1 of the embodiment, the synchronizing device S is used as the selection unit, which rotates the shaft and the gear integrally while synchronizing the rotational speed of the shaft and the rotational speed of the gear. The present invention is not limited to this, and any type can be used as long as the shaft and the gear can be rotated integrally, such as a type in which the shaft and the gear are directly connected.

  As mentioned above, although embodiment of this invention was described using the Example, this invention is not limited to such an Example, In the range which does not deviate from the summary of this invention, it can implement with a various form. Of course.

It is a schematic block diagram of a twin clutch type transmission.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Twin clutch type transmission 2 1st input shaft 3 2nd input shaft 4 Counter shaft 5 Output shaft 6, 6 ', 6''Ball bearing 7, 7', 7 '' Needle bearing 8 Transmission case 8a Front wall 8b Intermediate wall 8c Rear wall CS Crankshaft C1, C2 Clutch TM Speed change gear mechanism G Drive gear G1 1st speed drive gear G2 2nd speed drive gear G3 3rd speed drive gear G4 4th speed drive gear G6 6th speed drive gear GO Output gear (5-speed gear)
GR Reverse drive gear GC Output counter gear G 'Driven gear G1' 1st speed driven gear G2 '2nd speed driven gear G3' 3rd speed driven gear G4 '4th speed driven gear G6' 6th speed Driven gear GR 'Reverse driven gear S, S6, S24, S35, S1R Synchronizer

Claims (4)

A first input shaft to which the power of the internal combustion engine is input via the first clutch;
A second input shaft coaxially fitted to the first input shaft to which power of the internal combustion engine is input via a second clutch;
A twin clutch type transmission comprising: a gear mechanism that transmits the power input to the second input shaft to the output shaft with a first gear ratio;
The gear mechanism is
An idler gear loosely fitted to the first input shaft;
A fixed gear fixedly arranged on the output shaft that is always meshed with the idle gear;
A twin clutch type transmission comprising: selection means fixedly disposed on the second input shaft for selecting the idle gear and rotating the idle gear and the second input shaft together;   2. The idle gear according to claim 1, wherein the number of teeth is larger than that of the fixed gear so that the rotation speed of the second input shaft is increased and transmitted to the output shaft as the predetermined gear ratio. Twin clutch type transmission. The twin clutch transmission according to claim 1 or 2, wherein the transmission has six forward speeds.
The idle gear is a twin clutch transmission that is a gear that constitutes a sixth speed.   The selection means is means for rotating the idle gear and the second input shaft integrally while synchronizing the rotation speed of the idle gear with the rotation speed of the second input shaft. Item 4. The twin clutch transmission according to any one of items 3 to 4.

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