JP2000046127A - Vehicular transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To set the transmission ratio and the reverse gear ratio by providing first/fourth gears rotating together with an input shaft and second/third gears rotating together with an output shaft, and providing a planetray gear set, a fifth gear meshing with the first gear and a sixth gear meshing with the fourth gear on a reverse shaft. SOLUTION: An input shaft l transmits engine motive power, and an output shaft 2 is parallel to the shaft 1 to transmit motive power to a differential gear. A reverse shaft 3 converts motive power from the input shaft 1 into motive power at vehicle retreating time. A first gear 4 is fixed to the shaft 1 to rotate together with the shaft 1, and a second gear 5 meshes with a gear 1 to rotate together with the output shaft 2 by an engaging means 6. A third gear 7 is fixed to the output shaft 2, and a fourth gear 8 meshes with the gear 7 to rotate together with the input shaft l by an engaging means 8a. A planetary gear set 9 is arranged on the reverse shaft 3, and is integrally formed with a pinion 9a to transmit motive power to a sixth gear 11 from a fifth gear 10 through a reverse engaging means 12 at vehicle retreating time.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION The present invention relates to a vehicle transmission.
In particular, it is intended to reduce the size of the transmission (dimensions in the axial direction) and further increase the degree of freedom in setting the reverse gear ratio.

[0002]

2. Description of the Related Art A vehicle transmission includes a transmission mechanism for shifting the driving force of an engine, and an output gear for outputting the shifted driving force. The output gear is a ring of a wheel-side driving force transmission system. A transmission as disclosed in Japanese Utility Model Laid-Open Publication No. 6-73505 having a gear portion that meshes with a gear and a flange portion that supports the gear portion on both sides in the axial direction, or a gear that provides two forward gear ratios on the low speed side. A gear that is non-rotatably connected to the input shaft, a gear that provides the two forward gear ratios on the high-speed side is non-rotatably connected to the output shaft, and an idler gear is non-rotatably connected to the input shaft, and is driven. As disclosed in Japanese Patent Publication No. Hei 4-9933, a gear that is connected to form a low-speed side and is non-rotatably connected to the output shaft and that is driven to form a high-speed side gear ratio. Gears for automobiles with a simple structure The machine is known.

[0003]

The transmission disclosed in Japanese Utility Model Laid-Open Publication No. Hei 6-73505 has a structure in which the reverse gear is slid along the axial direction. There is a tendency that the length of the transmission tends to be longer, and the reverse gear is selectively slid, which may result in poor meshing of gears when the vehicle is retracted, resulting in poor operability. Was.

On the other hand, in the transmission disclosed in Japanese Patent Publication No. 4-9933, it is not necessary to secure an axial dimension for the reverse battle, so that the size of the transmission can be reduced (shaft). (Reduction of the dimension in the direction) and the gears are always meshed, so that a synchro mechanism can be applied, and the operability can be remarkably improved.

However, in the case of the transmission disclosed herein, when the arrangement of the shafts and the gear ratios of the first and third speeds are determined, the reverse gear ratio is determined in one way, and the degree of freedom in setting the reverse gear ratio is limited. Small (gear ratio is about 3.0-3.4)
However, there was a problem.

In addition, in the case of such a structure, when the reverse gear ratio is to be changed, it is necessary to exchange the idler gear or change the position of the idler gear. It is difficult to set the desired gear ratio. Also, two gear trains of the first speed and the third speed (two fixed gears 3 for the second speed of the input shaft,
Since a reverse load is introduced into the idler gear 4 and the corresponding idler gears 5 and 6) on the output shaft, the structure is currently strict in strength.

SUMMARY OF THE INVENTION An object of the present invention is to provide a new transmission which can be reduced in size in the axial direction and can be changed relatively easily without a large modification of the gear ratio or a change in the layout of components such as gears. Is to propose a machine.

[0008]

According to a first aspect of the present invention, there is provided a transmission having a plurality of gears arranged along the longitudinal direction of the shaft and having a plurality of gears arranged along the longitudinal direction of the shaft. An output shaft that has a plurality of gears arranged along the input shaft and engages with the gear of the input shaft to transmit the power of the engine to the differential gear under a predetermined gear ratio, and is arranged in parallel with these shafts from the input shaft. A transmission for a vehicle including a reverse shaft for converting transmitted power to power for reversing the vehicle, the transmission comprising a first gear fixedly held on an input shaft and rotating with the input shaft; A second gear meshing with the first gear and rotatable with the output shaft by the first engagement means and rotatable with the output shaft; a third gear fixedly held on the output shaft; Meshing with gear and rotating on input shaft A fourth gear capable of rotating with the input shaft by a second engagement means, the planetary gear set having a pinion gear, a ring gear, a carrier, and a sun gear; a first gear; A fifth gear meshing with a sixth gear meshing with a fourth gear is provided, and the power from the fifth gear is reversed through a planetary gear set to reverse the rotation direction only when the vehicle is reversing.
It is characterized in that a reverse engagement means for transmitting to the gear is provided.

In the transmission according to a second aspect of the present invention, in the configuration of the first aspect, the fifth gear is rotatable integrally with the sun gear of the planetary gear set when the gear is retracted.
Is made rotatable integrally with the ring gear of the planetary gear set.

The transmission according to claim 3 of the present invention is characterized in that the sixth gear is provided on the outer periphery of the ring gear in the structure of claim 2.

According to a fourth aspect of the present invention, there is provided the transmission according to the first aspect, wherein the reverse engagement means fixes the carrier of the planetary gear set to the transmission case when the vehicle retreats, so that when the vehicle retreats. It is characterized in that power is transmitted in the. Further, in the transmission according to claim 5 of the present invention, the reverse engagement means rotates the fifth gear rotatable on the reverse shaft together with the reverse shaft in synchronization with the reverse shaft in the configuration of claim 1 so that the reverse movement can be performed. It is characterized in that power is transmitted in the. Also,
According to a sixth aspect of the present invention, in the transmission according to the first aspect, the reverse engagement means synchronously rotates a sun gear rotatable on the reverse shaft with a fifth gear rotatable on the reverse shaft. It is characterized in that the motive power is transmitted when the vehicle is moving backward. A transmission according to a seventh aspect of the present invention is the transmission according to the first aspect, wherein the reverse engagement means includes a reverse shaft and a sixth shaft rotatable on the reverse shaft.
The power is transmitted when the vehicle moves backward by synchronously rotating the gears.

Further, a transmission according to claim 8 of the present invention is characterized in that the reverse engagement means in the structure of claim 1 or 4 employs a synchronization mechanism.

[0013]

The transmission according to the first aspect of the present invention does not slide the reverse gear in the axial direction, so that the size of the transmission can be reduced by that much, and the input shaft and the output can be reduced. Since the reverse shaft arranged in parallel with the shaft is provided with a planetary gear set having a pinion gear, a ring gear, and a sun gear that is integrated with the reverse shaft, the transmission gear ratio can be set in this planetary gear mechanism. Is possible,
The degree of freedom in setting the reverse gear ratio is large (the gear ratio is about 3.
(It can be changed within a range of 0 to 6.0). Further, since a reverse load is applied to the fourth gear rotatable with the input shaft and the third gear (one gear train) rotatably held on the output shaft, the load can be reduced (strength of strength is reduced). In terms of terms).

In the transmission according to the second aspect of the present invention, the fifth gear is rotatable integrally with the sun gear of the planetary gear set during reversing, and the sixth gear is integrated with the ring gear of the planetary gear set. Since it is rotatable, it is possible to reduce the speed by the planetary gear (for example, as compared with a case where the sixth gear is rotatable integrally with the sun gear and the fifth gear is integrally rotatable with the ring gear). T) A large gear ratio can be obtained.

In the transmission according to the third aspect of the present invention, the sixth gear is provided on the outer periphery of the ring gear in the configuration of the second aspect, which is advantageous in reducing the number of parts, and is advantageous in reducing the number of parts. There is an advantage that the configuration can be simplified.

In the transmission according to the fourth aspect of the present invention, the reverse power is transmitted by applying, for example, a synchromesh mechanism for fixing the carrier of the planetary gear mechanism to the transmission case when the reverse engagement means is retracted. When the vehicle is moving forward, the rotation of the pinion is set to 0, so that the strength required for the pinion is smaller than when the carrier is fixed at all times. Since relative rotation of components such as gears and carriers can be reduced, it is advantageous in terms of wear resistance, and so strict management is not required for lubrication and the like.

In the transmission according to a fifth aspect of the present invention, the reverse engagement means rotates the fifth gear rotatable on the reverse shaft together with the reverse shaft in synchronization with the reverse gear.
Further, in the transmission according to claim 6 of the present invention, the reverse engagement means is configured to synchronously rotate a sun gear rotatable on the reverse shaft and a fifth gear rotatable on the reverse shaft, thereby achieving the present invention. The transmission according to claim 7 of the present invention transmits power when the vehicle moves backward by rotating the reverse engagement means with the reverse shaft and the sixth gear rotatable on the reverse shaft. Therefore, in any case, when the reverse is selected, a poor meshing of the gear does not occur. In the transmission according to the eighth aspect of the present invention, the reverse engagement means is a synchronization mechanism, so that when the reverse is selected, poor meshing of gears does not occur and operability is improved.

[0018]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, the present invention will be described more specifically with reference to the drawings. FIG. 1 shows the structure of a transmission according to the first to fourth and eighth aspects of the present invention. In FIG. 1, reference numeral 1 denotes an input shaft for transmitting the power of an engine, An output shaft 3 that engages with the gears and transmits the power of the engine to the differential gear under a predetermined gear ratio, and 3 is a reverse shaft that converts the power transmitted from the input shaft 1 to the power when the vehicle moves backward. The reverse shaft 3 is arranged in parallel with the input shaft 1 and the output shaft 2.

Reference numeral 4 denotes a first gear fixed to the input shaft 1 and rotatable with the shaft 1. Reference numeral 5 denotes a second gear meshing with the first gear 4, and the second gear 5 is a first gear. Are rotatable together with the output shaft 2 by the engaging means (synchromesh mechanism) 6. Reference numeral 7 denotes a third gear, and the third gear 7 is fixed to the output shaft 2.

Reference numeral 8 denotes a fourth gear. The fourth gear 8 meshes with the third gear 7 and is rotatable on the input shaft 1, and the second engagement means (synchromesh mechanism) 8a
Thus, the input shaft 1 and the input shaft 1 can be rotated. Reference numeral 9 denotes a planetary gear set provided on the reverse shaft 3, and the planetary gear set 9 includes a pinion 9a, a ring gear 9b, and a carrier 9
c, and a sun gear 9d shown as an example integrated with the reverse shaft 3.

The planetary gear set 9 is mounted on the reverse shaft 3.
In addition, a fifth gear 10 meshing with the first gear 4 and a sixth gear 11 meshing with the fourth gear 8 are arranged. 12 is the fifth gear 10 only when the vehicle is moving backward.
Is a reverse engaging means for transmitting the power from the sixth gear 11 to the sixth gear 11, and the reverse engaging means 12 can apply a synchromesh mechanism or the like, and the carrier 9c of the planetary gear mechanism is attached to the transmission case by the engaging means 12. By fixing, the power at the time of retreating of the vehicle is transmitted, and by releasing the fixation of the carrier 9c, the transmission of power at the time of retreating is cut off.

In the transmission having the structure as shown in FIG. 1, a planetary gear shaft 9 is provided on the reverse shaft 3 so that when the vehicle retreats, the planetary gear set 9 is used to make a differential gear through the output shaft 2. Power is transmitted. With such a structure, the reverse shaft 3 does not need to adopt a configuration in which a gear disposed on the shaft is slid. The speed ratio can be adjusted over a range of approximately 3.0 to 6.0 by changing the number of teeth and the size of each gear in the planetary gear mechanism, so that the degree of freedom in setting the reverse gear ratio is increased. Will also be expanded.

Particularly in this example, the sixth gear 11 meshing with the fourth gear 8 is connected to the ring gear 9b of the planetary gear mechanism.
This configuration is effective in reducing the number of components and making the size compact.

FIG. 2 corresponds to the first to third, fifth, and eighth aspects. The fifth gear 10 is rotatably held with respect to the reverse shaft 3 via a bearing 10a. This shows an example of a transmission having the same structure as that of FIG. 1 except that the reverse engagement means 12 is disposed between the reverse engagement means 12 and the reverse shaft 3. 12, the fifth gear 10 and the reverse shaft 3 rotate synchronously, and the power for reversing the vehicle is transmitted to the sixth gear 11, and in this case also, the basic configuration of the transmission is There is no difference from the sign.

FIG. 3 corresponds to claims 1, 2, 4, and 8, wherein the sun gear 9d and the fifth gear 1 of the planetary gear mechanism are provided.
0 and the sun gear 9 d is rotated together with the fifth gear 10 by the reverse shaft 8 which rotates integrally with the sixth gear 11.
Reverse engagement means for holding the carrier 9c of the planetary gear mechanism to the transmission case so as to be rotatable above and transmitting the power from the fifth gear 10 to the sixth gear 11 only when the vehicle moves backward. In this example, the arrangement is basically the same as that of FIG. 1 except that the engaging means 12 acts on the carrier 9c.

FIG. 4 corresponds to the first, second, sixth, and eighth aspects of the present invention, and schematically shows the structure of the transmission. The reference numerals in FIG. 4 are the same as those in FIG. ing. In this example, the power from the input shaft 1 is transmitted to the sun gear 9 d of the planetary gear mechanism by the reverse engagement
a, power for reversing the vehicle on the reverse shaft 3 via the carrier 9c and the ring gear 9b is transmitted to the sixth gear 11. In this example as well, there is no need to move the reverse gear along the axis.
Similarly to the above, it is advantageous for size reduction,
Since the planetary gear mechanism is provided, the gear ratio can be set within a relatively wide range.

FIG. 5 corresponds to the first, second, seventh and eighth aspects of the present invention. The sixth gear 11 is rotatably held on a reverse shaft 3 via a bearing, and the reverse gear 3 is In this example, the sixth gear 11 is not provided with the ring gear 9b of the planetary gear mechanism, but is provided separately on the reverse shaft 3 in this example. Although the length of the reverse shaft 3 becomes slightly longer, it is not necessary to secure a dimension to slide the gears. Therefore, the reverse gear is slid to transmit power when the vehicle moves backward. The size can be reduced as compared with a conventional transmission.

Although FIGS. 1 to 5 show the case where the planetary gear mechanism disposed on the reverse shaft 3 employs a single pinion planetary gear set, the present invention may employ a double pinion planetary gear set. Needless to say.

[Brief description of the drawings]

FIG. 1 is a diagram showing a configuration of a transmission according to the present invention.

FIG. 2 is a diagram showing a configuration of a main portion of another transmission according to the present invention.

FIG. 3 is a diagram showing a configuration of another transmission according to the present invention with respect to main parts thereof.

FIG. 4 is a diagram schematically showing a configuration of another transmission according to the present invention.

FIG. 5 is a diagram schematically showing a configuration of another transmission according to the present invention.

[Explanation of symbols]

 REFERENCE SIGNS LIST 1 input shaft 2 output shaft 3 reverse shaft 4 first gear 5 second gear 6 first engagement means 7 third gear 8 fourth gear 9 planetary gear set 10 fifth gear 11 sixth gear 12 Reverse engagement means

 ──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Masahiko Yamada 2-12 Kawanami-cho, Atsuta-ku, Nagoya, Aichi Prefecture Inside Aichi Machine Industry Co., Ltd. Automobile Co., Ltd. (72) Inventor Tomoyuki Hara 2 Takaracho, Kanagawa-ku, Yokohama-shi, Kanagawa Prefecture Nissan Motor Co., Ltd. Inventor Kiyosei Yamamoto 2 Takaracho, Kanagawa-ku, Yokohama, Kanagawa Prefecture Nissan Motor Co., Ltd. F-term (reference) 3J028 EA25 EB35 EB62 FA06 FB05 FC42 FC44 FC64 GA02

Claims (8)

[Claims] 1. An input shaft having a plurality of gears arranged along a longitudinal direction of a shaft and receiving gears of an engine and having a plurality of gears arranged along the longitudinal direction of the shaft. An output shaft that transmits the power of the engine to the differential gear at a predetermined gear ratio, and a power that is disposed parallel to these shafts and that is transmitted from the input shaft and that is converted into power when the vehicle is retracted and output. A transmission for a vehicle having a reverse shaft transmitting to a shaft, wherein the transmission is fixedly held on an input shaft and rotates with the input shaft, and meshes with the first gear. A second gear rotatable with the output shaft by the first engagement means, a third gear fixedly held on the output shaft, and a second gear rotatable on the input shaft meshing with the third gear; Rotates with input shaft by engaging means And a potential of the fourth gear, the reverse shaft, the pinion gear, the planetary gear set and the first having a ring gear, carrier and sun gear
A fifth gear meshing with the fourth gear and a sixth gear meshing with the fourth gear are arranged, and the power from the fifth gear is reversed only through the planetary gear set to reverse the rotation direction only when the vehicle retreats. 6. A transmission for a vehicle, comprising reverse engagement means for transmitting to gear 6. The fifth gear is rotatable integrally with the sun gear of the planetary gear set, and the sixth gear is rotatable integrally with the ring gear of the planetary gear set when the vehicle is retracted. A transmission for a vehicle according to claim 1. 3. The transmission according to claim 2, wherein the sixth gear is provided on an outer periphery of the ring gear. 4. The vehicle transmission according to claim 1, wherein the reverse engagement means transmits power when the vehicle retreats by fixing the carrier of the planetary gear set to the transmission case when the vehicle retreats. 5. The vehicle transmission according to claim 1, wherein the reverse engagement means transmits power when the vehicle moves backward by synchronously rotating a fifth gear rotatable on the reverse shaft together with the reverse shaft. Machine. 6. A reverse engagement means for transmitting power when the vehicle retreats by synchronously rotating a sun gear rotatable on the reverse shaft as well as a fifth gear rotatable on the reverse shaft. Item 4. A transmission for a vehicle according to Item 1. 7. The vehicle according to claim 1, wherein the reverse engagement means transmits power when the vehicle moves backward by synchronously rotating a reverse shaft and a sixth gear rotatable on the reverse shaft. Transmission. 8. The vehicle transmission according to claim 1, wherein the reverse engagement means uses a synchronization mechanism.