JPH0611412Y2 - Manual transmission for vehicle - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial application] The present invention relates to a manual transmission for a vehicle.

[Prior art]

As one type of vehicle manual transmission, there is a type including a counter gear, a counter shaft, and other auxiliary shafts, an example of which is disclosed in Japanese Patent Publication No. 46-8647. In such a manual transmission, the input shaft and the output shaft are coaxially opposed to each other, and the auxiliary shaft is arranged in parallel to both of these shafts.

Another example of this type of manual transmission is the actual open sho 58.
In this manual transmission, an input shaft, an output shaft, and two auxiliary shafts are arranged in parallel with each other.

[Problems to be solved by the invention]

By the way, in the former transmission, since the input shaft and the output shaft are coaxially opposed to each other, the shaft length of the transmission is necessarily long and the output shaft is at a high position corresponding to the input shaft. There are various inconveniences when mounted on a vehicle, and various devises are required.

Further, in the latter transmission, since the shafts are arranged in parallel with each other, the output shaft overlaps with the input shaft in the axial direction and is located below the input shaft, and the disadvantage of the former transmission is eliminated. To be done. However, the latter transmission cannot be used as a multi-speed transmission because it has one shift stage for one auxiliary shaft, and the conventional transmission is used for such a multi-speed transmission. In the case of configuring, the transmission will be as large as or larger than the conventional one.

Therefore, an object of the present invention is a transmission for a multi-speed transmission, which has a short shaft length and allows the output shaft to be positioned at a desired portion in the vertical direction with respect to the input shaft, which is extremely suitable for mounting on a vehicle. It is to provide a convenient manual transmission.

[Means for solving problems]

The vehicle manual transmission according to the present invention includes an input shaft having a first drive gear for a low speed stage and a second drive gear for a high speed stage, which is rotatably supported in the case, and rotates in the case. An output shaft that is rotatably supported and arranged in parallel to the input shaft and that has a plurality of speed-driven gears for each shift stage, and that is rotatably supported in the same case and is parallel to both the shafts. A first driven gear for a low speed stage, which is disposed in the first drive gear and is engaged with the first drive gear, and a plurality of low speed drive gears which are engaged with the respective speed driven gears.
The auxiliary shaft is rotatably supported in the same case, is arranged in parallel to the three shafts, and is meshed with the second driven gear for high speed gear meshing with the second drive gear and each of the variable speed driven gears. A second counter shaft having a plurality of high speed drive gears, wherein a plurality of low speed drive gears on the first counter shaft and a plurality of high speed drive gears on the second counter shaft are speed-shifted on the output shaft; It is characterized in that the driven gears are shared with each other, and the remaining variable speed drive gear and the driven gears are housed in a clutch housing constituting the case and covered with a cover in the housing.

[Function and effect of device]

In the transmission having such a configuration, the power input to the input shaft is transmitted to the first counter shaft by the first drive gear and the first driven gear, and is transmitted to the second counter shaft by the second drive gear and the second driven gear. Then, these sub shafts are rotated. Therefore, if one of the plurality of low-speed drive gears included in the first sub-shaft is coupled to the sub-shaft, power is transmitted to the output shaft by the drive gear and the low-speed driven gear that meshes with the drive gear. It is output after being changed to columns. Further, if one of the plurality of high-speed drive gears of the second auxiliary shaft is connected to the same auxiliary shaft, power is transmitted to the output shaft by the drive gear and the high-speed driven gear that meshes with the drive gear, and each high speed stage Is changed to and output.

As described above, the transmission according to the present invention has a multi-speed shifting function, but since the shafts are arranged parallel to each other and overlap each other in the axial direction, the shaft length of the transmission is greatly shortened and the output shaft is It can be located at a desired portion in the vertical direction with respect to the input shaft. Particularly, in the present invention, since the plurality of low speed drive gears on the first counter shaft and the plurality of high speed drive gears on the second counter shaft share the speed driven gears on the output shaft, they are commonly used. It is possible to reduce the number of variable speed driven gears by the number of the output shafts and the output shaft and all other shafts related thereto. Moreover, since these gears are housed in the mission case that constitutes the case, and the remaining variable speed drive gear and driven gear are housed in the clutch housing that constitutes the case, the dead space of the housing is used effectively. The length of the case can be shortened, and the distance between the shaft support portions in each shaft can be shortened. Therefore, the transmission is very easily mounted on the vehicle regardless of the type of the vehicle. In addition, the remaining variable speed drive gear described above,
Since the driven gear is covered with the cover in the clutch housing, the meshing noise of these gears can be reduced.

〔Example〕

The first embodiment of the present invention will be described below with reference to the drawings.
FIG. 3 to FIG. 3 show a transmission for a front engine / front drive (FF) vehicle which is an embodiment of the transmission according to the present invention. 1 is a sectional view taken along the line I--I of FIG. 3, and FIG. 2 is a sectional view taken along the line II--II of FIG.

Therefore, the transmission TM includes an input shaft 11, an output shaft 12, first and second counter shafts 13 and 14, and a reverse idler shaft 25b described later, and each of these shafts is a case 15 including a clutch housing 15a and a transmission case 15b. It is housed in. The input shaft 11 is rotatably supported by the intermediate wall of the input shaft 11 and the rear end of the rear wall 15d through the tapered roller bearings 16a and 16b while penetrating the front wall 15c of the case 15. The output shaft 12 is located below the input shaft 11 and has front and rear walls 15c and 15d of the case 15.
And extends in the front-rear direction, and is rotatably supported by the front wall 15c at its tip end and the rear wall 15d at its rear end via tapered roller bearings 16c, 16d. The first counter shaft 13 is disposed on the right side of the input shaft 11 and the output shaft 12 in parallel with the shafts 11 and 12 and in the middle in the vertical direction, and has front and rear walls 15c and 15 at both ends thereof.
It is rotatably supported by d via tapered roller bearings 16f and 16g. The front end of the first counter shaft 13 slightly faces the clutch housing 15a. The second counter shaft 14 includes both shafts 11 and 12.
Is rotatably supported similarly to the first counter shaft 13 via the taper roller bearings 16h and 16i on the left side, and its tip faces the clutch housing 15a.

The input shaft 11 is integrally formed with two gears of a large diameter and a small diameter. The small diameter gear constitutes a first drive gear 21a for a low speed stage and the large diameter gear a second drive for a high speed stage. It constitutes the gear 22a. The first drive gear 21a constantly meshes with a first driven gear 21b integrally formed with the first counter shaft 13, and the second drive gear 22a is a second driven gear 22b integrally formed with the second counter shaft 14. Always meshes with. A first speed drive gear 23a and a second speed drive gear 23b are rotatably mounted on the first counter shaft 13 with the first synchromesh 31 interposed therebetween.
Each drive gear 23a, 23b is a synchromesh 31
By sliding the sleeve 31a in the axial direction, the sleeve 31a is selectively coupled to the first counter shaft 13 and, at the same time, is in a non-coupled state. In addition, the second counter shaft 14
Above is the third speed drive gear 23c and the fourth speed drive gear 23.
and d are rotatably assembled with the second synchromesh 32 sandwiched therebetween. The drive gears 23c and 23d are selectively coupled to the second counter shaft 14 and simultaneously brought into a non-coupled state by axially sliding the sleeve 32a of the synchromesh 32. In these counter shafts 13 and 14, the reverse drive gear 23f is integrally assembled to the front end portion of the first counter shaft 13, and the fifth speed drive gear 23e is rotatable at the tip end portion of the second counter shaft 14. , The third synchromesh 33 is assembled by a conventional method. The reverse drive gear 23f is housed in the clutch housing 15a, and the fifth speed drive gear 23e and the third synchromesh 33 are also housed in the clutch housing 15a. The fifth speed drive gear 23e is the third synchromesh 3
By sliding the third sleeve 33a in the axial direction, the connection with the second counter shaft 14 is interrupted. The gears 23e and 23f and the third synchromesh 33 are covered by a cover 15e assembled to the front wall 15c in the clutch housing 15a.

On the other hand, a large-diameter gear and a small-diameter gear are integrally formed on the output shaft 12, and the large-diameter gear is a drive gear 23a, 23c on both counter shafts 13, 14.
Is configured as a first speed, third speed driven gear 24a that always meshes with each other, and the small-diameter gear is configured as a second speed, fourth speed driven gear 24b that constantly meshes with both drive gears 23b, 23d. Further, on the output shaft 12, a fifth speed driven gear 24c is integrally attached to the tip thereof,
An output gear 24d is integrally formed between the driven gears 24b and 24c. 5th driven gear 2
4c is housed in the clutch housing 15a,
5th speed drive gear 23e is always meshed with and cover 15e
Is covered with. The output gear 24d meshes with the ring gear 41 of the differential 40, and the fifth speed driven gear 24c is the reverse idler gear 2.
It can be connected to the reverse drive gear 23f via 5a.

The reverse idler gear 25a is a front wall 15c of the case 15.
Further, the reverse idler shaft 25b rotatably supported between the covers 15e is assembled so as to be integrally rotatable and slidable in the axial direction, and is covered with the cover 15e. The reverse idler gear 25a slides in the axial direction by a shift fork (not shown) and simultaneously meshes with or disengages from the reverse idler gear 23f and the fifth speed driven gear 24c. On the other hand, in the differential 40, the ring gear 41 is mounted on the outer periphery of the differential case 42, and the power transmitted to the output shaft 12 is distributed from the side gears 43a and 43b to the side gear shafts 44a and 44b, so that the left and right gears (not shown) are provided. Output to the front wheel side.

In the transmission TM, the input shaft 11 is connected to the crankshaft of the engine via a clutch (not shown), and the output shaft 12 is connected to a rear propeller shaft (not shown).

In the transmission TM having such a configuration, when power from the engine is input to the input shaft 11, the power is transmitted to the first counter shaft 13 by the first drive gear 21a and the driven gear 21b, and
It is transmitted to the second counter shaft 14 by the second drive gear 22a and the driven gear 22b, and both counter shafts 13 and 14 rotate. In this state, by operating the first synchromesh 31, the first speed drive gear 23
When a is connected to the first counter shaft 13, the power of the counter shaft 13 is transmitted to the output shaft 12 as shown by the one-dot chain line a, and when the second speed drive gear 23b is connected to the first counter shaft 13, The power of the counter shaft 13 is transmitted to the output shaft 12 as shown by the chain line b. Further, by operating the second synchromesh 32, the third speed drive gear 23c
Is coupled to the second counter shaft 14, the power of the counter shaft 14 is transmitted to the output shaft 12 as indicated by a chain double-dashed line c, and the fourth speed drive gear 2
When 3d is connected to the second counter shaft 14, the power of the counter shaft 14 is transmitted to the output shaft 12 as indicated by the chain double-dashed line d. Furthermore, the third
By operating the synchromesh 33, the fifth speed drive gear 2
When 3e is connected to the second counter shaft 14, the power of the input shaft 11 is transmitted to the output shaft 12 as shown by a three-dot chain line e. Therefore, the power from the engine is shifted to the fifth forward speed, output from the output shaft 12 to the differential 40, and output to the front wheels through the side gear shafts 44a and 44b.

On the other hand, when the reverse idler gear 25a is slid to mesh with the reverse drive gear 23f and the fifth speed driven gear 24c, the power transmitted to the first counter shaft 13 is rotated in the reverse direction with respect to the input shaft 11, and the output shaft 12 is rotated. Be transmitted to. Therefore, the power is shifted to the reverse gear and output to the front wheels via the differential 40.

By the way, in the transmission TM, since the input shaft 11, the output shaft 12, and both the counter shafts 13 and 14 are all arranged in parallel to each other, the input shaft 11 and the output shaft 12 overlap each other in the axial direction. The axial length of the transmission is greatly reduced by the length. Therefore,
The transmission TM is smaller and lighter in weight, and more easily mounted on the vehicle.
Since the distance between the shaft support portions in 4 is shortened, it is possible to suppress the thermal influence on the preload of each taper roller bearing. Particularly, in the present embodiment, the first speed drive gear 23a on the first counter shaft 13 and the third speed drive gear 23c on the second counter shaft 14 commonly use the driven gear 24a on the output shaft 12, and these three gears are used. 23a, 23c and 24a are located in parallel with each other. Similarly, the second speed drive gear 23b on the first counter shaft 13 and the fourth speed drive gear 23d on the second counter shaft 14 share the driven gear 24b on the output shaft 12 with each other, and these three gears 23b, 23d, 24b are located in parallel with each other. Further, the fifth speed driven gear 24c on the output shaft 12 also serves as the reverse driven gear. Therefore, it is possible to reduce the number of shared shift driven gears, and it is possible to eliminate a single reverse driven gear. Furthermore, each gear 23
e, 23f, 24c, 25b, etc. are the clutch housing 1
The housing 1 is housed in the housing 5a and the cover 1 is housed in the housing 15a.
It is covered by 5e. Therefore, the dead space of the clutch housing 15a can be effectively used as a housing portion for the gears to reduce the axial length of the shafts 11 to 14 in the mission case 15b, and the shafts of the housings 15a can be shortened. The axial length in the mission case 15b can be shortened without increasing the directional length. Therefore, the length of the transmission TM in the axial direction can be further shortened, the distance between the shaft supporting portions of the shafts 11 to 14 can be further shortened, and further, the meshing noise of each gear can be reduced. it can.

FIG. 4 shows a shift example of the reverse gear train. The reverse gear train of this modified example is of a constant mesh type, and the reverse drive gear 23g is rotatably assembled on the first counter shaft 13 and the fourth synchromesh 34 assembled on the same shaft 13. The connection with the shaft 13 is interrupted by the sleeve 34a. Also, the reverse idler gear 25c is the reverse idler shaft 25.
It is integrally assembled to the d and is always meshed with the reverse drive gear 23g and the fifth speed driven gear 24c.

Although the example of the transmission for the FF vehicle is shown in the above embodiment, the differential 40 and the output gear 24d of the above embodiment are omitted in the present invention, and the output shaft 12 is used.
The front engine / rear drive (FR) is configured by extending and connecting to the rear propeller shaft.
It can be a transmission for a car.

[Brief description of drawings]

FIG. 1 is a sectional view of a transmission according to an embodiment of the present invention taken along the line I--I of FIG. 3, and FIG. 2 is a sectional view taken along the line II--II of FIG. 3 of the same transmission. 3 is a layout view of each shaft in the transmission, and FIG. 4 is a partial cross-sectional view showing a modified example of the reverse gear train. Explanation of reference numerals 11 ... Input shaft, 12 ... Output shaft, 13, 14 ... Counter shaft, 15 ... Case, 15a ... Clutch housing, 15b ... Mission case, 15d ... Cover, 21a, 22a.
Drive gear, 21b, 22b ... Driven gear, 23
a-23e ... 1st-5th drive gears, 23f, 23
g ... Reverse drive gear, 24a, 24b ... 1st-4th driven gear, 24c ... 5th driven gear, 2
4d ... Output gear, 25a, 25c ... Reverse idler gear, 25b, 25d ... Reverse idler shaft, 40 ... Differential.

Claims (1)

[Scope of utility model registration request] 1. An input shaft rotatably supported in a case, the input shaft having a first drive gear for a low speed stage and a second drive gear for a high speed stage, and rotatably supported in the same case. An output shaft that is arranged parallel to the input shaft and has a plurality of shift driven gears for each shift stage, and an output shaft that is rotatably supported in the same case and that is arranged parallel to the both shafts. A first driven shaft having a low speed stage that meshes with a drive gear and a plurality of low speed drive gears that mesh with each of the variable speed driven gears; and the three shafts that are rotatably supported in the same case. A second high speed stage which is arranged parallel to the second drive gear and meshes with the second drive gear.
A second counter shaft having a driven gear and a plurality of high speed drive gears meshing with the respective speed driven gears; a plurality of low speed drive gears on the first counter shaft and a plurality of high speed drive drives on the second counter shaft; And a gear that shares a speed-driven driven gear on the output shaft with each other, and the remaining speed-changing drive gear and driven gear are housed in a clutch housing that constitutes the case and are covered by a cover in the housing. Machine.