JP2001082554A - Automobile transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To shorten the axial length of automobile toothed-gear transmissions having between themselves and engines two clutches whose alternate engagement and disengagement enables shifts without an interruption of driving force. SOLUTION: A countershaft 22 parallel with a first input shaft 16 and a second input shaft 20 is connectable to the first input shaft 16 via the 1st gear pair 26a, 26b and to the second input shaft 20 via the 2nd gear pair 30a, 30b, and is connected to an output shaft 24 via driving gears 44a and 44b. The output shaft 24 is connectable to both first and second input shafts 16 and 20 via the 3rd gear pair 34a, 34b, to the first input shaft 16 via the 4th gear pair 40a, 40b, and to the second input shaft 20 via the 5th gear pair 42a, 42b. Between the first and second input shafts 16 and 20 on one hand and the countershaft 22 on the other, a first dog clutch 28 and a second dog clutch 32 are respectively axially overlapped with a third dog clutch 36 and a fourth dog clutch 38.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention has two clutches between an engine and a transmission, and can alternately connect and disconnect the two clutches to change the speed without interrupting the driving force. The present invention relates to an automotive gear transmission, a so-called twin clutch type automotive transmission.

[0002]

2. Description of the Related Art Conventionally, as a gear transmission for an automobile capable of shifting without interrupting the driving force by alternately connecting and disconnecting two clutches, a magazine "Motor Fan", October 1987, The one described on page 70 is known.
In the above conventional example, a torque converter is not required, the first, third and fifth odd stages are driven via the first clutch, and the second and fourth even stages are driven via the second clutch. It is configured to drive the gears, and by alternately connecting and disconnecting the first clutch and the second clutch, the automatic transmission can be performed without interruption of the driving force. Therefore, the power transmission efficiency is higher than that of a normal automatic transmission with a torque converter. Is high.

In the above-described conventional example, the first clutch for driving the odd-numbered stage and the second clutch for driving the even-numbered stage are alternately connected and disconnected to automatically shift the speed.
In this case, the transmission gear pair cannot be connected unless the clutch on the speed side to be subsequently engaged by the shift command is disengaged, so that the shift between the first and third speeds and the shift between the second and fourth speeds are performed. As described above, even if an attempt is made to perform a so-called one-step jump shift between odd-numbered steps or even-numbered steps to enable a quick shift, both clutches must be disengaged during the shift, and the driving force is interrupted. There is a problem that it is practically impossible to set a one-step jump speed.

The present inventor has disclosed Japanese Patent Application Laid-Open No. 58-118355,
Japanese Patent Application Laid-Open No. Sho 60-65541 and Japanese Patent Publication No. 6-8569 propose means for solving this problem. These inventions
The third speed drive can be performed from either the first clutch or the second clutch, and the first clutch can be driven in the first speed, the fourth speed,
The second clutch is configured to be capable of driving at the second speed and the fifth speed. As a result, the above-described one-step jump shift can be quickly performed without interruption of the driving force.

[0005]

However, in the conventional example and the above-mentioned invention, the axial length of the transmission is increased, and particularly in the case of a front-wheel drive vehicle in which the engine is placed sideways (the engine is arranged at right angles to the vehicle traveling direction). In the above, the space for the clutch and the transmission is limited, so that there is an obstacle in implementing the invention.

Accordingly, the present invention provides a twin-clutch type automatic transmission in which the transmission can be made compact, and in particular the axial length of the transmission, while enabling quick one-step jumping without interruption of the driving force. It is an object of the present invention to reduce the length of the vehicle so that it can be easily mounted on a front-wheel-drive vehicle with an engine mounted horizontally.

Another object of the present invention is to enable the above-mentioned one-step jumping without interrupting the driving force even in a six-speed forward transmission. The present invention includes a transmission having six or more forward gears.

[0008]

In order to achieve the above object, in a vehicle transmission according to the present invention, the driving force of an engine is transmitted to a first input shaft via a first clutch. The second input shaft can be transmitted to the second input shaft via a second clutch, and the first input shaft and the auxiliary shaft arranged in parallel to the second input shaft are connected to the first input shaft via a first speed gear pair. ,
In addition, the second input shaft can be connected to the second input shaft via a second speed gear pair, and the sub shaft is connected to the output shaft via a drive gear, and the output shaft is connected to the first and second input shafts. At least 4th and 5th gear pairs are provided, each shift being the first
It is performed by alternate connection and disconnection of the clutch and the second clutch.

According to a second aspect of the present invention, there is provided the transmission for an automobile, wherein the output shaft is connected to the first input shaft and the second input shaft via the third speed gear pair, and the fourth speed gear pair is connected to the output shaft. And a second input shaft via a fifth speed gear pair.

According to a third aspect of the present invention, at least one of the third speed gear pairs constitutes a driving gear for connecting the countershaft and the output shaft. I do.

According to a fourth aspect of the present invention, at least one of the four-speed gear pairs constitutes a driving gear for connecting the countershaft and the output shaft. I do.

According to a fifth aspect of the present invention, there is provided a transmission for an automobile, wherein the countershaft and the first-speed gear can be connected via a one-way clutch.

According to a sixth aspect of the present invention, there is provided a vehicle transmission according to the present invention, wherein a first speed gear on the countershaft, a fourth speed gear on the first input shaft or a third speed gear on the second input shaft. Are configured to be connectable via a reverse gear.

According to a seventh aspect of the present invention, the first speed gear on the countershaft is connected to the fourth speed gear or third speed gear on the output shaft via a reverse gear. It is characterized by being configured to be possible.

According to the present invention, the driving force of the engine is transmitted to the first input shaft via the first clutch and to the second input shaft via the second clutch. And a third speed gear pair that can be connected to either the first input shaft or the second input shaft, and a third speed input gear and an output shaft that meshes with the third speed input gear or a sub shaft that is connected to the output shaft. And a third-speed output gear selectively connectable to one of the three-speed output gears. The sixth-speed output gear meshes with the third-speed input gear or the sixth-speed input gear rotating integrally therewith, and the sixth-speed output gear is connected to the output shaft or the It is characterized in that it can be selectively connected to one of the sub shafts connected to the output shaft.

[0016]

In the vehicle transmission according to the present invention, the driving force of the engine is transmitted to the first input shaft via the first clutch and to the second input shaft via the second clutch. The first input shaft and the second input shaft are arranged in parallel to each other, and the auxiliary shaft is connected to the first input shaft via the first speed gear pair and to the second input shaft via the second speed gear pair. And a counter shaft is connected to the output shaft via a drive gear, and at least a fourth speed and a fifth speed gear pair are provided between the output shaft and the first and second input shafts. Since each shift is performed by alternately connecting and disconnecting the first clutch and the second clutch, the first and second speeds drive by driving the output shaft from the first or second input shaft via the auxiliary shaft and the drive gear. Fourth and fifth speed drives drive the output shaft directly from the first or second input shaft.

Further, in the vehicle transmission according to the present invention, the output shaft is connected to the first gear via the third speed gear pair.
To the input shaft and the second input shaft, and to the first through a fourth speed gear pair.
The second input shaft and the second input shaft can be connected to the input shaft via a fifth speed gear pair, so that the second input shaft and the second speed gear pair or the third speed gear are driven while the first input shaft is driven at the first speed. The first input shaft and the fourth speed gear pair or the third speed gear pair are selectively connected to each other while the fifth gear pair is selectively connected and driven at the fifth speed from the second input shaft. The first input shaft is connected to the first speed gear pair, the third speed gear pair, or the fourth speed gear pair in the state of being driven at the second speed from.

According to a third aspect of the present invention, at least one gear of the third speed gear pair constitutes a drive gear for connecting the auxiliary shaft and the output shaft. As a result, in the first or second speed drive, the output shaft is driven from the countershaft via at least one of the drive gear and the third speed gear pair.

According to a fourth aspect of the present invention, at least one of the four-speed gear pairs constitutes a drive gear for connecting the countershaft and the output shaft. As a result, in the first or second speed drive, the output shaft is driven from the countershaft via the drive gear and at least one gear of the fourth speed gear pair.

In the vehicle transmission according to the present invention, the countershaft and the first-speed gear can be connected via a one-way clutch. It is driven via a clutch, and is switched to the 2nd speed, and at the same time, the 1st speed is automatically released.

According to a sixth aspect of the present invention, there is provided a vehicle transmission according to the present invention, wherein a first speed gear on the countershaft, a fourth speed gear on the first input shaft or a third speed gear on the second input shaft. Since the gears can be connected to each other via a reverse gear, when the vehicle is traveling in reverse, the first gear on the sub shaft is shifted to the reverse gear and the fourth gear on the first input shaft or the third gear on the second input shaft. The output shaft is driven in reverse rotation via gears.

According to a seventh aspect of the present invention, there is provided a transmission for an automobile according to the present invention, wherein the first gear on the countershaft and the fourth gear on the output shaft are provided.
Since the speed gear or the third speed gear is configured to be connectable via a reverse gear, at the time of reverse travel, the first speed gear on the counter shaft is driven through the reverse gear and the fourth speed gear or the third speed gear on the output shaft. To drive the output shaft in reverse rotation.

Further, in the vehicle transmission according to the present invention, the driving force of the engine is transmitted to the first input shaft via the first clutch and to the second input shaft via the second clutch. A third speed gear pair, which can be transmitted to the input shaft and can be connected to any of the first input shaft and the second input shaft, is connected to the third speed input gear and the output shaft or the output shaft. A third-speed output gear selectively connectable to one of the countershafts, the sixth-speed output gear meshing with a third-speed input gear or a sixth-speed input gear rotating integrally therewith;
Since the high-speed output gear can be selectively connected to one of the output shaft and the countershaft connected to the output shaft, when one of the output shaft or the countershaft is connected to the third-speed output gear, the first input shaft and the third input shaft are connected. When driving at the third speed on any of the two input shafts and connecting one of the output shaft or the countershaft to the sixth speed output gear, driving at the sixth speed on either the first input shaft or the second input shaft do.

[0024]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below with reference to the drawings. In the following description, a distinction between a and b is provided at the end of the symbol for each gear of the gear pair.
Represents a gear on the input side (drive side), and b represents a gear on the output side (driven side).

FIG. 1 is a skeleton diagram of a main part of an automotive transmission according to the present invention. A first input shaft 16 is transmitted from the engine 10 to the transmission 12 via a first clutch 14.
Further, it is possible to input a driving force to the second input shaft 20 which is a hollow shaft via the second clutch 18. Each pair of speed change gears is provided between the first input shaft 16 and the second input shaft 20 and the sub shaft 22 and the output shaft 24 provided in parallel with the first input shaft 16 and the second input shaft 20.

That is, the 1 connected to the first input shaft 16
The speed gear pair 26a, 26b can be connected to the countershaft 22 via the first dog clutch 28, and likewise the second input shaft 2
The second speed gear pair 30a, 30b connected to the gear 0 can be connected to the counter shaft 22 via the second dog clutch 32. Also, a third speed gear pair 34a, 34b connected to the output shaft 24
Is connected to the first input shaft 16 via the third dog clutch 36.
And the second input shaft 20 via the fourth dog clutch 38.
Can be connected separately or simultaneously.

Further, the fourth speed gear pair 40a, 40b connected to the output shaft 24 can be connected to the first input shaft 16 via the third dog clutch 36, and the fifth gear pair 40a, 40b is connected to the output shaft 24 in the same manner. The speed gear pairs 42 a and 42 b can be connected to the second input shaft 20 via the fourth dog clutch 38.
That is, the third dog clutch 36 meshes with the third speed gear 34a when shifted to the right, and meshes with the fourth gear 40a when shifted to the left. In addition, the fourth dog clutch 38
Shifts to the left, meshes with the third gear 34a, and shifts to the right, meshes with the fifth gear 42a.

A pair of drive gears 44a connected to the countershaft 22;
44b meshes with the third speed gear 34b. In the figure, the drive gear 44b is drawn apart from the third speed gear 34b,
Both are engaged. Also, the reverse gear pair 46a, 46
b is connected to the output shaft 24 via the fourth speed gear 40b, and is connected to the first speed gear 26 via the first dog clutch 28.
b. That is, the first dog clutch 2
8 shifts to the right to connect the first speed gear 26b to the countershaft 22, and shifts to the left to link the first speed gear 26b and the reverse gear 46a. In the figure, the fourth speed gear 40b and the reverse gear 46b are drawn apart,
Both are engaged.

The first to fourth dog clutches 28, 32,
Each of 36 and 38 is provided with a synchronization mechanism for smooth engagement, but is not shown. Also, the first in the figure
The fourth to fourth dog clutches 28, 32, 36, 38 are in a neutral state and do not transmit power. The output shaft 24 drives left and right axles 54a, 54b via reduction gears 50a, 50b and a differential device 52,
54b is connected to wheels (not shown).

Next, the operation of the transmission having the above configuration will be described. First, the start in the forward first speed is performed by shifting the first dog clutch 28 to the right by setting the first gear 2.
6b and the sub shaft 22 are connected, and the first clutch 14 is gradually connected. That is, the driving force of the engine 10 is transmitted to the first input shaft 16 via the first clutch 14, and the first gear pair 26a, 26b, the driving gear pair 44a, 44b connected to the sub shaft 22, and the third gear pair. Gear 34b
Is transmitted to the output shaft 24 via the The first clutch 14 is gradually connected for smooth start, and the output shaft 2
Reference numeral 4 drives left and right wheels (not shown) via a reduction gear pair 50a, 50b, a differential device 52, and axles 54a, 54b, and the vehicle starts and starts accelerating.

Next, the shift from the first gear to the second gear will be described. After driving the second speed gear 30b and the sub shaft 22 by the second dog clutch 32 while driving at the first speed,
By switching off the power transmission by the first clutch 14 and gradually connecting the second clutch 18, the drive is switched to the second speed drive.

That is, the driving force of the engine 10 is
The power is transmitted to the second input shaft 20 via the clutch 18 and transmitted to the output shaft 24 via the second speed gear pair 30a, 30b and the driving gear pair 44a, 44b connected to the auxiliary shaft 22, and further via the third speed gear 34b. You. Here, the first-speed drive is performed until the power transmission by the first clutch 14 is interrupted, and the second-speed drive is switched when the second clutch 18 is connected, so that the connection / disconnection control of the first clutch 14 and the second clutch 18 is appropriately performed. By doing so, the shift from the first speed to the second speed can be performed without interruption of the driving force.

Subsequently, the shift from the second speed to the third speed is performed by the first dog clutch 28 in the driving state at the second speed.
Is returned to neutral, the third dog clutch 36 is shifted to the right to connect the first input shaft 16 and the third speed gear 34a, and then the power transmission by the second clutch 18 is cut off and the first By gradually connecting the clutch 14, the drive is switched to the third speed drive. The driving force of the engine 10 is transmitted to the first input shaft 16 via the first clutch 14 and transmitted to the output shaft 24 via the third speed gear pair 34a, 34b. Also in this case, since the second speed is switched to the third speed by the connection / disconnection control of the second clutch 18 and the first clutch 14, the speed change is performed without interruption of the driving force.

Subsequently, when shifting from the third speed to the fourth speed,
In the above-described third-speed driving state, the second dog clutch 32 is disconnected in advance and the fourth dog clutch 38 is shifted to the left to connect the second input shaft 20 and the third-speed gear 34a. The second clutch 18 is connected. In this case, the third speed gear 34a is temporarily connected to the engine 10 via the first and second clutches 14, 18.

In this state, the power transmission of the first clutch 14 is temporarily stopped, the third dog clutch 36 is shifted to the left to connect the first input shaft 16 and the fourth speed gear pairs 40a, 40b, and then the second clutch 18 and the first clutch 14 is connected again. Thereby, the driving force of the engine 10 is transmitted to the first input shaft 16 via the first clutch 14 and transmitted to the output shaft 24 via the fourth speed gear pair 40a, 40b, thereby switching to the fourth speed drive. . Also in this case, the second clutch 18 and the first clutch 1
Since the gear is switched from the third gear to the fourth gear by the connection / disconnection control of 4, the shift is performed without interruption of the driving force.

Subsequently, when shifting from the fourth speed to the fifth speed, the fourth dog clutch 38
Is shifted to the right to connect the second input shaft 20 and the fifth speed gear 42a, and then the power transmission by the first clutch 14 is cut off, and the second clutch 18 is gradually connected to drive the fifth speed. Switch to The driving force of the engine 10 is transmitted to the second input shaft 20 via the second clutch 18 and
The power is transmitted to the output shaft 24 via the speed gear pairs 42a and 42b. Also in this case, the first clutch 14 and the second clutch 1
Since the gear is switched from the fourth speed to the fifth speed by the connection / disconnection control of No. 8, the shift is performed without interruption of the driving force.

The above is a case where the gears are sequentially shifted to the upper gear, such as the first gear to the second gear, and the second gear to the third gear. When shifting to lower gears in sequence, control may be performed in the reverse order. However, depending on the driving conditions of the automobile, there may be a case where a so-called one-step jump shift is required, such as the first to third speeds or the fourth to second speeds. Hereinafter, such a one-step jump shift will be described.

First, in shifting from the 1st speed to the 3rd speed, the fourth dog clutch 38 is shifted to the left in the driving state at the 1st speed to connect the second input shaft 20 and the 3rd speed gear 34a. After that, the power transmission by the first clutch 14 is cut off, and the second clutch 18 is gradually connected to switch to the third speed drive. The shift from the third gear to the first gear can be performed in the reverse order. Also in these cases, the connection and disconnection control of the first clutch 14 and the second clutch 18
Since the shift between the third speed and the third speed is performed, the driving force is not interrupted during acceleration, and the reverse driving force from the output shaft 24 to the engine 10 is interrupted even during so-called engine braking. The shift is performed without accompanying.

Next, the shift between the second speed and the fourth speed is performed by connecting the auxiliary shaft 22 and the second speed gear 30b by the second dog clutch 32, and connecting the first input shaft 1 by the third dog clutch 36.
In the state where the sixth and fourth speed gears 40a are connected, the second speed and the fourth speed are controlled by the connection / disconnection control of the first clutch 14 and the second clutch 18.
Shifts between high speeds can be made. The shift between the third speed and the fifth speed is performed by connecting the first input shaft 16 and the third speed gear 34a by the third dog clutch 36, and connecting the second input shaft 20 and the fifth speed gear by the fourth dog clutch 38. With the connection with the clutch 42a, the shift between the third speed and the fifth speed can be performed by controlling the connection and disconnection of the first clutch 14 and the second clutch 18.

In these, the third speed gear 34a is connected to the first input shaft 1
Driving can be performed from any of the sixth and second input shafts 20, and the second and fifth speeds can be driven from the second input shaft 20, and the first and fourth speeds can be driven from the first input shaft 16, respectively. This is made possible by the above.

Next, the reverse drive will be described. In this case, the first dog clutch 28 is shifted to the left to connect the reverse gear 46a and the first speed gear 26b,
By gradually connecting the first clutch 14, it is possible to perform acceleration from the start of reverse rotation as in the case of the first speed drive. That is, the driving force of the engine 10 is transmitted to the first input shaft 16 via the first clutch 14, and the first speed gear pairs 26a, 26
b to the reverse gear pair 46a, 46b and the fourth gear 40b
Is transmitted to the output shaft 24 as a reverse rotation driving force.

As described above, in the embodiment shown in FIG. 1, the shift can be performed without interruption of the driving force, and similarly, the one-step jump shift can be performed without interruption of the driving force. Therefore, the vehicle can be appropriately driven under all conditions. These are suitable for providing an automatic transmission by automating the shift operation of the first to fourth dog clutches 28, 32, 36, 38 and the connection / disconnection control of the first and second clutches 14, 18. .

The configuration shown in FIG. 1 comprises a first input shaft 16 and a second input shaft 20 and a sub-shaft 22 arranged in parallel with them.
Between the first speed gear pair 26a, 26b and the second speed gear pair 30
a and 30b, the first dog clutch 28 and the second dog clutch 32 are arranged on the auxiliary shaft 22, and the third dog clutch 36 and the fourth dog clutch 38 are connected to the first input shaft 14 and the second input shaft. Arranged on the shaft 20 and the first
The dog clutch 28 and the third dog clutch 36 overlap in the axial direction, and the second dog clutch 32 and the fourth
Since the dog clutch 38 and the dog clutch 38 can be arranged so as to overlap each other in the axial direction, the first and second input shafts 1 are simply provided.
6, 20 and the output shaft 24, all the dog clutches are provided, and the dog clutches are arranged on adjacent shafts so as not to overlap each other. Can be shortened.

However, simply arranging the dog clutch so as to overlap the adjacent shafts,
If a synchronization mechanism (not shown) is provided for each of them, the diameter of the dog clutch portion increases, and for example, the first input shaft 1
6 and the distance between the second input shaft 20 and the countershaft 22 tends to be long. Therefore, if the drive gear 44a and the third speed gear 34a are simply meshed with each other, the drive gear 44a
Since the diameter of “a” becomes large, it becomes difficult to appropriately set the speed ratios of the first speed and the second speed.

However, the driving gear 44a and the third speed gear 34b
Are engaged with each other via the drive gear 44b,
By reducing the diameter of the drive gear 44a, it is possible to appropriately set the speed ratios of the first speed and the second speed. Further, since the reverse gear pair 46a, 46b for the reverse drive is provided so as to overlap the gear train for the forward drive, the reverse drive can be performed without increasing the axial length of the transmission.

With the above construction, the axial length of the transmission 12 is reduced, and the first and second clutches 1
Even if 4 and 18 are provided, the whole becomes compact and can be applied to a general front wheel drive vehicle. Further, as described above, the first clutch 1
4, the second clutch 18 is used only for shifting with small absorbed energy, so that the size of the second clutch 18 can be reduced, which contributes to making the whole compact.

FIG. 2 is a skeleton diagram showing another embodiment of the automotive transmission according to the present invention. Here, a description will be given mainly of portions different from the embodiment shown in FIG. 1, and description of substantially the same portions will be omitted. A first input shaft 16 and a second input shaft 20, a sub shaft 22 and an output shaft 2
1 and 5 are arranged in the same manner as in the embodiment shown in FIG.
The connection between a and 44b is different. That is, one drive gear 44b is integrally connected to the third speed gear 34a, and the sub shaft 22 and the output shaft 24 are always connected to each other via the drive gear pair 44a, 44b and the third speed gear pair 34a, 34b. ing.

The auxiliary shaft 22 and the output shaft 24 are similar to those shown in FIG.
Since the two gears are connected by meshing, the rotation direction is the same, and the transmission of power is basically the same. The first speed gear 26b and the sub shaft 22 can be connected via a one-way clutch 62. In the figure, the sleeve 28a of the first dog clutch 28 is located at the center, and the first speed gear 26b and the sub shaft 22 are connected by a one-way clutch. A state of being connected via 62 is shown, and this state may be in principle as it is except for reverse.

The one-way clutch 62 can transmit only the driving force in the direction of accelerating the vehicle, and can rotate freely in the opposite direction. When the sleeve 28a is moved to the right, the first speed gear 26b and the countershaft 22 are mechanically connected to each other, so that power can be transmitted in both acceleration and deceleration. When the first gear 26b is moved to the left, the connection between the first gear 26b and the countershaft 22 is released, and the first gear 26b and the reverse gear 46a are connected.

Therefore, when starting and accelerating at the first speed, it is only necessary to connect the first clutch 14 in the state shown in the figure. Speed gear 26b and countershaft 2
2 is mechanically connected. In the state shown in the figure, when shifting from the state of acceleration at the first speed with the first clutch 14 connected to the second speed, the second dog clutch 32 is shifted to the second speed gear 3.
It is only necessary to engage the second clutch 18 by engaging with the second clutch 18.

That is, by the operation of the one-way clutch 62, the first-speed drive is performed until the second clutch 18 is connected. When the second clutch 18 is connected, the drive is switched to the second speed and the first-speed drive is automatically performed. The driving state is released. For this reason, a shift shock or the like is unlikely to occur, and a smooth shift from the first speed to the second speed can be performed. Therefore, similarly to the embodiment shown in FIG. 1, in the embodiment shown in FIG.
Since it is possible to perform one-step jump shifting, the vehicle can be appropriately driven under all conditions.

Further, since the first dog clutch 28 and the third dog clutch 36 are arranged to overlap in the axial direction, and the second dog clutch 32 and the fourth dog clutch 38 are arranged to overlap in the axial direction, The axial length of the entire machine can be reduced. Further, since the reverse gear pair 46a, 46b for the reverse drive is provided so as to overlap the gear train for the forward drive, the reverse drive can be performed without increasing the axial length of the transmission.

FIG. 3 is a skeleton diagram showing another embodiment of the automotive transmission according to the present invention. Here, a description will be given mainly of portions different from the embodiment shown in FIG. 1, and description of substantially the same portions will be omitted. A first input shaft 16 and a second input shaft 20, a sub shaft 22 and an output shaft 2
A gear pair of the first to fifth speeds is arranged between the gears 4 and 4 in the same manner as in the embodiment of FIG. 1, except that the counter shaft 22 and the reduction gear 50b are connected. In other words, the drive gear 44 integrated with the countershaft 22 meshes with the reduction gear 50b, although they are drawn apart in the figure. For this reason, the countershaft 22 does not pass through the output shaft 24 and the reduction gear 50 b
Power can be transmitted to the auxiliary shaft 22 from the first input shaft 16 and the second input shaft 20 in the first and second speeds.
The driving force transmitted to directly drives the reduction gear 50b.

Therefore, the sub shaft 22 and the output shaft 24 are connected via the drive gear 44 and the reduction gear pair 50a, 50b. The reverse gear 46 can be connected to the first speed gear 26b, as in FIG. 1, but meshes with the third speed gear 34b. Although not shown in the drawing, the reverse gear 46 meshes with the third speed gear 34b. As a result, the first input shaft 16
From the first gear pair 26a, 26b and the reverse gears 46, 3
The output shaft 24 is driven to rotate in the reverse direction via the speed gear 34b. Although the power transmission path from the countershaft 22 to the reduction gear 50b is different, the rotation direction is the same as that of the embodiment shown in FIG.
Power transmission is basically the same.

Therefore, similarly to the embodiment shown in FIG. 1, in the embodiment shown in FIG. 3, it is needless to say that the shift can be performed sequentially without interruption of the driving force. The vehicle can be properly driven under the conditions. Further, since the first dog clutch 28 and the fourth dog clutch 38 are arranged so as to overlap in the axial direction, the axial length of the entire transmission can be reduced. Further, since the reverse gear 46 for reverse drive is provided so as to overlap with the gear train for forward drive, reverse drive is possible without increasing the axial length of the transmission.

FIG. 4 is a skeleton diagram showing another embodiment of the automotive transmission according to the present invention. Here, a description will be given mainly of portions different from the embodiment shown in FIG. 1, and description of substantially the same portions will be omitted. A speed change gear pair is provided between the first input shaft 16 and the second input shaft 20, and the sub shaft 22 and the output shaft 24 provided in parallel to the first input shaft 16 and the second input shaft 20, but this configuration is different from FIG.

That is, the first speed gear pair 26a, 26b connected to the first input shaft 16 can be connected to the sub shaft 22 by the first dog clutch 28, but the third speed gear 34 meshed with the first speed gear 26a outputs. It is arranged on the shaft 24 and can be connected to the output shaft 24 by a third dog clutch 36. Further, a pair of second speed gears 30a and 30 connected to the second input shaft 20 are provided.
b can be connected to the auxiliary shaft 22 by the second dog clutch 32, but a fifth speed gear 42 meshed with the second speed gear 30a is disposed on the output shaft 24, and can be connected to the output shaft 24 by the third dog clutch 36. It is.

The fourth speed gear pair 4 connected to the output shaft 24
4a and 40b can be connected to the first input shaft 16 by a fourth dog clutch 38, and can be connected to another output shaft 24.
The speed gear pairs 34a 'and 34b' can be connected to the second input shaft 20. A third-speed drive from the first input shaft 16 by a third-speed gear 34 meshed with the first-speed gear 26a;
The gear ratio is the same as that of the third-speed driving from the second input shaft 20 by another third-speed gear pair 34a ', 34b' connected to the fourth gear 4 except for the power transmission path.

The driving gear pair 44a, 44b is
The second and fourth speed gears 40a are connected. For this reason, the sub shaft 22 and the output shaft 24 are always connected via the drive gear pairs 44a and 44b and the fourth speed gear pairs 40a and 40b.
The reverse gears 46a and 46b provided in parallel with the sub shaft 22 can be connected by a sixth dog clutch 56. The reverse gear 46a is connected to the first speed gear 26b and the reverse gear 46.
b meshes with the drive gear 44a. Further, the first speed gear 26b and the countershaft 22 can be connected via the first dog clutch 28 and also via the one-way clutch 62 and the seventh dog clutch 60.

That is, similarly to the embodiment shown in FIG. 2, the one-way clutch 62 can transmit power only in the direction of accelerating the vehicle, and always connects the seventh dog clutch 60 to the first-speed gear 26b except for reverse. And can be connected. Thus, in the case of normal acceleration, the first-speed drive can be performed by simply connecting the first clutch 14 without connecting the first dog clutch 28, and the state of the first-speed drive via the one-way clutch 62 At
When the second dog clutch 32 is connected and the second clutch 18 is connected, the mode is switched to the second speed.

With the above configuration, in addition to the third speed gear 34 drivable from the first input shaft 16, another pair of third speed gears 34a 'and 34b' drivable from the second input shaft 20 are provided. Although the transmission path is slightly different from that in FIG. 1, the connection relationship between each transmission gear and the first and second clutches 14 and 18 is the same.
Therefore, similarly to the embodiment shown in FIG. 1, in the embodiment shown in FIG. 4, it is needless to say that the shift that is sequentially performed without interruption of the driving force can be a one-step jump shift.
The vehicle can be properly driven under all conditions.

The first speed input gear 26 related to the first speed drive
a also serves as an input gear related to the third speed drive, the second speed input gear 30a related to the second speed drive also serves as an input gear related to the fifth speed drive, and the first dog clutch 28 and the second dog clutch 32 Since the third dog clutch 36 and the third dog clutch 36 are arranged so as to overlap in the axial direction, the axial length of the entire transmission can be reduced. Further, since the reverse gear pair 46a, 46b for reverse drive is provided so as to overlap with the gear train for forward drive, reverse drive is possible without increasing the axial length of the transmission.

Next, FIG. 5 is a skeleton diagram showing another embodiment of the transmission for an automobile according to the present invention. FIG.
Is a six-speed forward transmission, which will be described mainly with respect to portions different from the embodiment shown in FIGS. 1 and 2, and description of substantially the same portions will be omitted. The connection relationship between the first speed gear pairs 26a, 26b, the second speed gear pairs 30a, 30b, the fourth speed gear pairs 40a, 40b, and the fifth speed gear pairs 42a, 42b is the same as that of the embodiment shown in FIGS. , Drive gear pair 44a, 4
The connection relation of 4b is the same as that of the embodiment shown in FIG.

Of the third speed gear pairs 34a and 34b, 34a
2 is integrated with the drive gear 44b as in FIG. 2, and can be connected to either the first input shaft 16 or the second input shaft 20. The third speed gear 34b is connected to the fifth dog clutch 48 by the fifth dog clutch 48. A sixth speed gear 58, which is connectable to the output shaft 24 and meshes with the drive gear 44b, is provided on the output shaft 24, and is configured to be connectable to the output shaft 24 by shifting the fifth dog clutch 48 to the right. I have.
That is, in this case, the drive gear 44b functions as a sixth speed input gear, and the fifth dog clutch 48 can selectively connect the output shaft 24 to the third speed gear 34b or the sixth speed gear 58.

Therefore, when the third speed gear 34b and the output shaft 24 are connected by the fifth dog clutch 48,
1 and 2, a third speed drive is possible, but the fifth dog clutch 48 allows the sixth speed gear 58 and the output shaft 24 to be driven.
When these are connected, six-speed driving becomes possible.

That is, when the sixth speed gear 58 and the output shaft 24 are connected, when the first input shaft 16 and the third speed gear 34a are connected by the third dog clutch 36, the first input shaft 16 When the output shaft 24 is driven via the drive gear 44 b and the sixth speed gear 58, and the second input shaft 20 and the third speed gear 34 a are connected by the fourth dog clutch 38, the drive gear is transmitted from the second input shaft 20. The output shaft 24 is driven via the 44b and the sixth speed gear 58, and a gear ratio of 6th speed is obtained in each case.

As described above, the sixth speed as well as the third speed can be driven from either the first input shaft 16 or the second input shaft 20, so that one step is skipped like a shift between the fourth speed and the sixth speed. The shift can be performed quickly without interruption of the driving force.
Further, a reverse gear pair 46a provided in parallel with the sub shaft 22,
46b is connectable by a sixth dog clutch 56, the reverse gear 46a meshes with the first speed gear 26b, and the reverse gear 46b meshes with the drive gear 44b. In the figure, the reverse gear 46b and the drive gear 44b are illustrated as being separated from each other, but they are engaged with each other.

Therefore, when the pair of reverse gears 46a and 46b are connected by the sixth dog clutch 56, the first input shaft 16 transmits the pair of first speed gears 26a and 26b, and the pair of reverse gears 46a and 46b.
a, 46b, a drive gear 44b and a third gear pair 34a,
The output shaft 24 is driven to rotate in the reverse direction via 34b.

As described above, in the embodiment of FIG. 5, as in the embodiment shown in FIG. 1, the shift can be performed without interrupting the driving, and the one-step jump can be performed. The vehicle can be properly driven under all conditions by utilizing the six-speed gear ratio. Further, since the first dog clutch 28 and the fifth dog clutch 48 are arranged so as to overlap in the axial direction, the axial length of the entire transmission can be reduced. Further, since the reverse gear pair 46a, 46b for the reverse drive is provided so as to overlap the gear train for the forward drive, the reverse drive can be performed without increasing the axial length of the transmission.

Further, although it is not possible to perform one-step jump shifting,
In a state where the sixth speed gear 58 and the output shaft 24 are connected,
When the first dog clutch 28 connects the first speed gear 26b and the sub shaft 22 or when the second dog clutch 32 connects the second speed gear 30b and the sub shaft 22,
Driving at speed ratios other than the first to sixth speeds is possible, but detailed description is omitted.

FIG. 6 is a skeleton diagram showing another embodiment of the automotive transmission of the present invention. FIG.
Is also a six-speed forward transmission, and the following description focuses on differences from the embodiment shown in FIGS. First gear pair 26a, 26b, second gear pair 30a, 30b, and fourth gear pair 40a, 40
The connection relationship of b is the same as the embodiment shown in FIGS.

The fifth-speed gear pairs 42a and 42b are connected to the output shaft 24 in the same manner as in the embodiment shown in FIGS.
The fifth input gear 20 can be connected to the second input shaft 20 by the fourth dog clutch 38, the fifth speed gear 42a is integrated with the drive gear 44b, and the drive gear pair 44a, 44b connected to the second input shaft 20 The sub shaft 22 and the output shaft 24 are connected via the speed gear pairs 42a and 42b.

The third speed gear 34a can be connected to the first input shaft 16 by the third dog clutch 36 and to the second input shaft 20 by the fourth dog clutch 38, and can be engaged with the third speed gear 34a. The gear 34 b can be connected to the countershaft 22 by a fifth dog clutch 48.
The sixth speed gear 58 meshed with the sixth dog clutch 56
Can be connected to the output shaft 24.

Therefore, the third speed gear 34 a is connected to the first dog clutch 36 or the fourth dog clutch 38
In a state where the third gear 34 b and the auxiliary shaft 22 are connected to each other by the fifth dog clutch 48 while being connected to the input shaft 16 or the second input shaft 20.
Are connected to the first input shaft 16 or the second input shaft 20, the third speed gear pair 34a, 34b drive gear pair 44a,
When the third speed drive is performed via the 44b-fifth gear pair 42a, 42b and the sixth speed gear 58 and the output shaft 24 are connected by the sixth dog clutch 56, the first input shaft 16 or the second input shaft 20 Sixth speed driving is performed via the third speed gear 34a and the sixth speed gear 58.

As described above, the sixth speed as well as the third speed can be driven from either the first input shaft 16 or the second input shaft 20, so that the sixth speed can be skipped by one step like the speed change between the fourth speed and the sixth speed. The shift can be performed quickly without interruption of the driving force.

The reverse gear pair 46a, 46b provided in parallel with the output shaft 24 can be connected by a seventh dog clutch 60. The reverse gear 46a meshes with the first speed gear 26a, and the reverse gear 46b It is in mesh with the speed gear 40b. In the figure, the reverse gear 46a and the first speed gear 26a are drawn apart, but they are meshed. Therefore, the reverse gear pair 46a is driven by the seventh dog clutch 60.
And 46b, the output shaft 24 is driven in reverse rotation from the first input shaft 16 via the first speed gear 26a, the reverse gear pair 46a, 46b, and the fourth speed gear 40b.

As described above, also in the embodiment of FIG. 6, as in the embodiment shown in FIG. 1, the shift can be performed without interrupting the driving, and the shift by one step can be performed. The vehicle can be properly driven under all conditions by utilizing the six-speed gear ratio.

Further, since the first dog clutch 28 and the third dog clutch 36 and the fourth dog clutch 38 and the fourth dog clutch 48 are arranged to overlap in the axial direction, the overall length of the transmission in the axial direction is increased. Can be shortened. Further, since the reverse gear pair 46a, 46b for reverse drive is provided so as to overlap with the gear train for forward drive, reverse drive is possible without increasing the axial length of the transmission.

FIG. 7 is a skeleton diagram showing another embodiment of the automotive transmission according to the present invention. FIG.
Is a six-speed transmission for driving the rear wheels, which is different from the embodiment shown in FIGS. 1 and 5, and the description of substantially the same parts is omitted. FIG. 7 illustrates the engine 10 on the left side in accordance with a general rear-wheel drive transmission. The first input shaft 16 connected to the first clutch 14 and the sub shaft 22 provided in parallel with the second input shaft 20 connected to the second clutch are connected to the drive gear pair 4.
4a and 44b are connected to the output shaft 24.

First speed gear pair 2 connected to first input shaft 16
6a and 26b are connected to the countershaft 22 by the first dog clutch 28.
The second speed gear pair 30a, 30b connected to the second input shaft 20 can be connected to the sub shaft 22 by the second dog clutch 32. The third speed gear pair 34a, 34b and the sixth speed gear pair 58a, 58b are provided adjacent to each other, the third speed gear 34a and the sixth speed gear 58a are integrally connected, and the first dog clutch 36 The input shaft 16 and the fourth dog clutch 38 allow the second input shaft 20
The countershaft 22 is connected to the third gear 34b or the sixth gear 58b by the fifth dog clutch 48.
And can be selectively connected.

Therefore, similarly to FIGS. 1 and 6, when the fifth dog clutch 48 is shifted to the left to connect the third speed gear 34b and the auxiliary shaft 22, the first input shaft 16 and the second input shaft The third speed drive is possible from any of the shafts 20. When the fifth dog clutch 48 is shifted to the right to connect the sixth speed gear 58b and the sub shaft 22, the first input shaft 16 and the second Sixth speed driving is possible from any of the input shafts 20. The fourth speed gear pair 40a, 40b is connected to the countershaft 22 and is connected to the second input shaft 2 by a fourth dog clutch 38.
Can be connected to 0.

The first input shaft 16 and the output shaft 24 can be connected by a sixth dog clutch 56. By connecting the first input shaft 16 and the output shaft 24, the first input shaft 16 and the output shaft 24 are directly connected.
High-speed drive is performed. The reverse gears 46a and 46b provided in parallel with the sub shaft 22 can be connected by a seventh dog clutch 60, the reverse gear 46a meshes with the first speed gear 26b, and the reverse gear 46b meshes with the drive gear 44b. In the figure, the reverse gear 46b and the drive gear 44b are drawn apart, but they are meshed.

Therefore, when the reverse gears 46a and 46b are connected by the seventh dog clutch 60, the first input shaft 16 causes the pair of first speed gears 26a and 26b,
The reverse drive is performed via the 46b drive gear 44b. The output shaft 24 drives wheels via a differential device or the like (not shown). As described above, in the embodiment of FIG. 7 as well, the power transmission path is partially different, but the third speed and the sixth speed can be driven from either the first input shaft 16 or the second input shaft 20. .

Therefore, similarly to the embodiment shown in FIGS. 1 and 5, the shift can be performed without interruption of the drive, and the shift can be performed by one step, and the gear ratio of six steps can be used. The vehicle can be properly driven under all conditions.

FIG. 8 is a skeleton diagram showing another embodiment of the automotive transmission according to the present invention. FIG.
This is also a six-speed transmission for rear-wheel drive, and will be described mainly with respect to portions different from the embodiment shown in FIG. 7, and description of substantially the same portions will be omitted. The only difference from FIG. 7 is the 5-speed drive.

That is, the fifth speed gear pair 42 connected to the countershaft
The first and second input shafts a and 42b can be connected to the first input shaft 16 by a third dog clutch 36, and the fifth input gear pair 42a and 42b and the drive gear pair 44
The output shaft 24 is driven at the 5th speed via a and 44b. That is, in FIGS. 7 and 5 in which the first input shaft 16 and the output shaft 24 are directly connected.
Other connection relationships are the same, only the speed ratio is different.

Therefore, similarly to the embodiment shown in FIG. 7, it is possible to carry out gear shifting without interruption of driving, and it is possible to carry out one-step jumping, and to make use of the six-speed gear ratio under all conditions. The vehicle can be appropriately driven.

The above-described embodiments are all applied to the third speed or the third speed.
The first and second clutches 18 and 18 are capable of driving at a high speed and a sixth speed, and can perform one-step jump shifting. However, according to the present invention, a plurality of dog clutches are overlapped in the axial direction. The purpose of this arrangement is to reduce the axial length of the transmission so that the transmission can be easily mounted on a vehicle such as a front wheel drive vehicle. Needless to say, even if the second clutch 18 and the second clutch 18 can be driven in odd and even stages, respectively, the length of the transmission in the axial direction can be similarly reduced.

The vehicle drive system of the present invention supports the respective shafts in the case of the transmission based on the general knowledge of those skilled in the art, so that the bearings can be appropriately arranged and the optimal automatic transmission can be performed. In addition, the present invention can be implemented in a mode in which changes and improvements are made, such as equipping a control device and an actuator for performing a shift operation and a clutch operation.

[0090]

As described above, according to the vehicle drive device of the present invention, the following effects can be obtained. (1) According to the vehicle driving apparatus of the present invention, the driving force of the engine is transmitted to the first input shaft via the first clutch and to the second input shaft via the second clutch. The countershafts, which can be transmitted respectively, are arranged in parallel to the first input shaft and the second input shaft to the first input shaft via the first speed gear pair and to the second input shaft via the second speed gear pair. Each of them is connectable, and the counter shaft is connected to the output shaft via a drive gear, and at least a fourth speed and a fifth speed gear pair are provided between the output shaft and the first and second input shafts. Since the speed change is performed by alternately connecting and disconnecting the first clutch and the second clutch, the dog clutch on the countershaft related to the first- or second-speed drive and the first or second gear related to the fourth- or fifth-speed drive are provided. Of the dog clutches on the two input shafts, at least one pair of dog clutches Since the transmission can be arranged to overlap in the axial direction, the transmission can be configured to be short in the axial direction.

(2) According to the vehicle driving apparatus of the present invention, the output shaft is connected to the first input shaft and the second input shaft via the third speed gear pair, and the fourth speed gear is provided. The first input shaft can be connected to the first input shaft via a pair, and the second input shaft can be connected to the second input shaft via a fifth speed gear pair. The gear is selectively connected to the third gear when driving at high speed, and 4 when driving at second speed.
1st and 3rd gear,
It is possible to quickly perform a one-step jump shift between the second speed, the fourth speed, and the third speed and the fifth speed.

(3) According to the vehicle driving apparatus of the third aspect of the present invention, at least one of the third speed gear pairs constitutes a driving gear for connecting the sub shaft and the output shaft. As a result, the dog clutch on the counter shaft related to the first- or second-speed drive and the first clutch related to the fourth- or fifth-speed drive
By disposing the dog clutch on the second input shaft and the dog clutch on the second input shaft so as to overlap each other in the axial direction, the axial length of the transmission is reduced, and the distance between the auxiliary shaft and the first and second input shafts is reduced. , The speed ratios of the first and second speeds can be set to appropriate values.

(4) According to the vehicle driving apparatus of the fourth aspect of the present invention, at least one of the gears of the fourth speed gear pair forms a driving gear for connecting the sub shaft and the output shaft. Therefore, the input gear related to the 1st or 2nd speed drive and the input gear related to the 3rd and 5th speed drive can be shared to reduce the axial length of the entire transmission.

(5) According to the vehicle driving apparatus of the present invention, the auxiliary shaft and the first-speed gear can be connected via the one-way clutch, so that the one-way acceleration is achieved during the first-speed acceleration. It is driven via the clutch, and when the gear is switched to the 2nd gear, the 1st gear is automatically released.
The shift from the first gear to the second gear can be performed smoothly.

(6) According to the vehicle driving apparatus of the present invention, the first speed gear on the countershaft and the fourth speed gear on the first input shaft or the third speed gear on the second input shaft are provided. Since the gears can be connected via the reverse gear, a reverse gear train can be configured without increasing the axial length of the transmission.

(7) According to the vehicle driving apparatus of the present invention, the first speed gear on the counter shaft and the fourth or third gear on the output shaft are connected via the reverse gear. As a result, the reverse gear train can be formed without increasing the axial length of the transmission.

(7) According to the vehicle driving apparatus of the present invention, the driving force of the engine is transmitted to the first input shaft via the first clutch and to the second input shaft via the second clutch. A third speed gear pair, which can be transmitted to the input shaft and can be connected to any of the first input shaft and the second input shaft, is connected to the third speed input gear and the output shaft or the output shaft. A third-speed output gear selectively connectable to one of the countershafts, the sixth-speed output gear meshing with a third-speed input gear or a sixth-speed input gear rotating integrally therewith;
Since the high-speed output gear can be selectively connected to one of the output shaft and the sub-shaft connected to the output shaft, between the first speed and the third speed, the second speed and the fourth speed can be achieved while the forward six-speed shift is possible. During the speed,
It is possible to quickly perform a one-step jump shift, such as between the third and fifth speeds and between the fourth and sixth speeds.

[Brief description of the drawings]

FIG. 1 is a skeleton diagram of a vehicle transmission according to the present invention.

FIG. 2 is a skeleton diagram of another embodiment of the vehicle transmission according to the present invention.

FIG. 3 is a skeleton diagram of another embodiment of the vehicle transmission according to the present invention.

FIG. 4 is a skeleton diagram of another embodiment of the automotive transmission according to the present invention.

FIG. 5 is a skeleton diagram of another embodiment of the automotive transmission according to the present invention.

FIG. 6 is a skeleton diagram of another embodiment of the automotive transmission according to the present invention.

FIG. 7 is a skeleton diagram of another embodiment of the automotive transmission according to the present invention.

FIG. 8 is a skeleton diagram of another embodiment of the automotive transmission according to the present invention.

[Explanation of symbols]

 10: Engine 12: Transmission 14: First clutch 16: First input shaft 18: Second clutch 20: Second input shaft 22: Secondary shaft 24: Output shaft 26: 1st gear, 1st gear pair 28: 1st gear 1 dog clutch 30: 2nd gear, 2nd gear pair 32: 2nd dog clutch 34: 3rd gear, 3rd gear pair 36: 3rd dog clutch 38: 4th dog clutch 40: 4th gear, 4th gear Pair 42: 5th gear, 5th gear 44: Drive gear, drive gear 46: Reverse gear, reverse gear 48: Fifth dog clutch 50: Reduction gear, reduction gear 52: Differential 54: Axle 56 : 6th dog clutch 58: 6th gear, 6th gear pair 60: 7th dog clutch 62: one-way clutch

Claims (8)

[Claims] An engine driving force can be transmitted to a first input shaft via a first clutch, and to a second input shaft via a second clutch, respectively.
A sub shaft arranged in parallel with the input shaft can be connected to the first input shaft via a first speed gear pair and to the second input shaft via a second speed gear pair, respectively. A fourth gear and a fifth gear are provided between the output shaft and the first and second input shafts, the first and second clutches being connected to each other through a drive gear; An automotive transmission characterized in that the transmission is executed by alternately connecting and disconnecting. 2. The output shaft is connected to the first input shaft and the second input shaft via a third speed gear pair, to the first input shaft via a fourth speed gear pair, and to a fifth speed gear. The second through a pair
The automotive transmission according to claim 1, wherein the transmission is configured to be connectable to each of the input shafts. 3. The transmission for an automobile according to claim 1, wherein at least one of the gears of the third speed gear pair forms the drive gear that connects the countershaft and the output shaft. Machine. 4. The vehicle transmission according to claim 1, wherein at least one gear of the fourth speed gear pair forms the drive gear that connects the countershaft and the output shaft. Machine. 5. The automotive transmission according to claim 1, wherein the countershaft and the first speed gear are connectable via a one-way clutch. 6. The first speed gear on the countershaft and the first speed gear,
The fourth gear on the input shaft or 3 on the second input shaft
6. The transmission for an automobile according to claim 1, wherein the transmission is connected to the speed gear via a reverse gear. 7. The apparatus according to claim 1, wherein said first speed gear on said counter shaft and said fourth speed gear or third speed gear on said output shaft are connectable via a reverse gear. 6. The automotive transmission according to any one of claims 1 to 5. 8. The driving force of the engine can be transmitted to a first input shaft via a first clutch and to a second input shaft via a second clutch, respectively. The third-speed gear pair connectable to any of the shafts comprises a third-speed input gear and a third-speed output gear meshing with the third-speed input gear and selectively connectable to one of the output shaft and a sub-shaft connected to the output shaft. A sixth-speed output gear meshes with the third-speed input gear or a sixth-speed input gear that rotates integrally therewith, and the sixth-speed output gear is selectively connected to one of the output shaft or a sub-shaft connected to the output shaft. An automotive transmission characterized by being connectable.