JPH04300442A - Planetary gear line of automatic transmission - Google Patents

Abstract

PURPOSE:To obtain multiple stages of speed number and set a plurality of number speeds under a over-driving condition by adding a pair of simple planetary gear mechanism. CONSTITUTION:A plurality lines of planetary gears BG composed of two pairs of simple planetary gear mechanisms, an additional planetary gear G3, first to fifth clutches C1 to C5, first and second brakes B1, B2, first to third one-way clutches WC1 to WC3 are arranged between an input shaft N and an output shaft U. The plural lines of planetary gear lines BG are composed of a first simple planetary gear mechanism G1 and an amplified stage planetary gear G2. An advance sixth speed and a back first speed are obtained by selectively operating the brakes, clutches, and one-way clutches. A transmission ratio of the fifth and sixth speed is under a over-driving condition.

Description

[Detailed description of the invention]

0001

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a planetary gear train for an automatic transmission that increases the number of gears by adding a set of simple planetary gear mechanisms.

0002

BACKGROUND OF THE INVENTION Conventional planetary gear trains for automatic transmissions include, for example, Japanese Patent Application Laid-Open No. 60-57036 and Japanese Patent Application Laid-Open No. 60-60-57036.
There is one described in 88252 publication.

These systems add one set of simple planetary gear mechanisms to a double-row planetary gear train consisting of two sets of simple planetary gear mechanisms, and are equipped with seven friction elements consisting of brakes and clutches. As a result, the number of gears is multi-staged, resulting in five forward speeds and one reverse speed.

0004

[Problem to be Solved by the Invention] Recently, there has been a social demand for reducing the fuel consumption rate of vehicles due to environmental issues and other reasons.

However, the conventional planetary gear train of the automatic transmission described above has a problem in that it is only possible to obtain one gear in an overdrive state, which reduces the fuel consumption rate. The present invention was made with attention to the above-mentioned problems, and by adding a set of simple planetary gear mechanisms, it is possible to increase the number of gears and set a plurality of gears in an overdrive state. It is intended to be.

[0006]

[Means for Solving the Problems] In order to achieve the above object, the planetary gear mechanism of the automatic transmission of the present invention includes a speed increasing planetary gear consisting of a set of simple planetary gear mechanisms, and another planetary gear connected to the planetary gear. A double-row planetary gear train that has a planetary gear mechanism and obtains an overdrive speed by operating the speed-increasing planetary gear, and an additional planetary gear train consisting of another set of simple planetary gear mechanisms. By adding a gear, the input shaft and the planet carrier of the speed increasing planetary gear can be connected, and the planet carrier of the speed increasing stage planetary gear and the sun gear of the additional planetary gear can be connected, and the speed increasing stage planetary gear The ring gear and the ring gear of the additional planetary gear are connected, and both the speed increasing stage planetary gear and the sun gear of the additional planetary gear can be respectively fixed to a stationary part, and the planet carrier of the additional planetary gear and the output shaft are connected. In the planetary gear train of the connected automatic transmission, the gear ratio of the speed increasing planetary gear is set to be larger than the gear ratio of the additional planetary gear.

[0007] The gear ratio of the speed increasing stage planetary gear is set to be larger than 0.45, the gear ratio of the additional planetary gear is set to less than 0.4, and (1+gear ratio of the additional planetary gear)/(1+speed increasing gear ratio). It is preferable to set the value of the gear ratio (gear ratio of the step planetary gear) to less than 0.9.

[0008]

[Operation] By adding one set of simple planetary gear mechanisms to a double gear train consisting of two sets of planetary gear mechanisms, the number of gears can be increased.

At this time, when only the speed-up stage planetary gear and the additional planetary gear are operated, by fixing both the sun gears of the speed-up stage planetary gear and the additional planetary gear, (1+gear ratio of the additional planetary gear)/ It is possible to obtain a gear ratio of (1+gear ratio of the planetary gear of the speed increasing stage). In addition, by fixing the sun gear of the speed increasing planetary gear and connecting the planet carrier of the speed increasing stage planetary gear with the sun gear of the additional planetary gear (1+
A gear ratio of (gear ratio of the additional planetary gear)/(1+gear ratio of the speed-increasing stage planetary gear+gear ratio of the additional planetary gear) can be obtained.

The latter gear ratio is an overdrive gear ratio regardless of the gear ratio of the gear ratio of the gear-up planetary gear and the gear ratio of the additional planetary gear, but the former gear ratio is the gear ratio of the gear ratio of the gear-up planetary gear. The overdrive state may not occur depending on the gear ratio of the additional planetary gear and the gear ratio of the additional planetary gear. In the present invention, by setting the gear ratio of the step-up planetary gear to be larger than the gear ratio of the additional planetary gear, both gear ratios are reliably brought into an overdrive state.

[0011] It is also possible to operate only the speed increasing planetary gear without activating the additional planetary gear to further increase the number of speeds in the overdrive state. Note that the double-row planetary gear train is not limited to one consisting of two sets of planetary gear mechanisms, and may be three or more sets, or may be one set.

Further, in the gear ratio of the speed increasing planetary gear and the gear ratio of the additional planetary gear, the gear ratio of the speed increasing stage planetary gear is set to be greater than 0.45, and the gear ratio of the additional planetary gear is set to 0.45.
If the value of (1+gear ratio of additional planetary gear)/(1+gear ratio of speed-up stage planetary gear) is set to less than 0.9, transition to overdrive state and overdrive will occur. The difference between gears in the drive state becomes an appropriate value, enabling smooth gear changes in the overdrive state.

[0013]

Embodiments Hereinafter, embodiments of the present invention will be explained based on the drawings. FIG. 1 is a diagram showing a first embodiment of a planetary gear train of an automatic transmission according to the present invention.

First, to explain the configuration, N in the figure refers to an input shaft connected to an output shaft on the engine side (not shown).
U indicates the output shaft, and between the input shaft N and the output shaft U, there is a double-row planetary gear train BG consisting of two sets of simple planetary gear mechanisms G1 and G2, and one set of simple planetary gear mechanisms. Additional planetary gears, first to fifth clutches C1 to C5, first and second brakes B1, B2, and first to third one-way clutches WC1
~WC3 is provided.

The double-row planetary gear train BG is composed of a first simple planetary gear mechanism G1 and a second simple planetary gear mechanism G2 which is an amplification stage planetary gear. Sun gear S1, first ring gear R1 and first
The second simple planetary gear mechanism G2 consists of a second sun gear S2, a second ring gear R2, and a second planet carrier PC2.

Further, the additional planetary gear is composed of a third simple planetary gear mechanism G3, and the third simple planetary gear mechanism G3 is composed of a third sun gear S3, a third ring gear R3, and a third planet carrier PC3.

The input shaft N is connected to a first ring gear R1, and is connected to a first sun gear S via a first clutch C1 arranged in parallel with the first ring gear R1.
1. The input shaft N is a first
The second sun gear S2 is also intermittently connected to the second sun gear S2 via the third clutch C3 or the first one-way clutch WC1 connected in series with the clutch C1.
can be fixed to a stationary part via the first brake B1. Further, the input shaft N is also connected intermittently to the second planet carrier PC2 via a fourth clutch C4 arranged in parallel with the third clutch C3. The second planet carrier PC2 can be fixed to the case K, which is a stationary part, via the second one-way clutch WC2, and is also connected in an intermittent manner to the third sun gear S3 via the fifth clutch C5. The third sun gear S3 can be fixed to the case K, which is a stationary part, via the second brake B2 or the third one-way clutch WC3.

[0018] Furthermore, the first planet carrier PC1 is
The second ring gear R2 and the third ring gear are connected via the second clutch C2.
A third planet carrier PC3 is connected to the output shaft U and is intermittably connected to the ring gear R3 and meshes with the third ring gear R3.

In the planetary gear train of the automatic converter having the above configuration, each brake B1, B2, clutches C1 to C5, and one-way clutches WC1 to WC3 are selectively operated in the combination shown in FIG. 2(a). , Figure 2(b)
Six forward speeds and one reverse speed shown in can be obtained.

[0020] In Fig. 2(a), a circle mark indicates a fastened state, and a blank mark indicates an open state. Further, α1 is the first sun gear S1 relative to the number of gears of the first ring gear R1.
α2 represents the ratio of the number of gears of second sun gear S2 to the number of gears of second ring gear R2, α3
is the third sun gear S with respect to the number of gears of the third ring gear R3
It represents the ratio of the number of gears of 3.

In the fifth and sixth gears, as shown in FIG. 2, the second simple planetary gear mechanism G2, which is a speed-increasing planetary gear, and the third simple planetary gear mechanism, which is an additional planetary gear mechanism. Only mechanism G3 operates, and in 5th gear, the 2nd and 3rd
By fixing sun gears S2 and S3, (1+α3)/(
A gear ratio of 1+α2) is obtained. Further, in the sixth speed, the second sun gear S2 is fixed and the second planet carrier PC2 is fixed.
By connecting the third sun gear S3 to (1+α3)/(
A gear ratio of 1+α2+α3) is obtained.

[0022] At this time, since α2, which is the gear ratio of the speed increasing planetary gear, is set larger than α3, which is the gear ratio of the additional planetary gear, the gear ratio at the fifth and sixth speeds is in an overdrive state. become. In this way, it is possible to set two gears in the overdrive state.

[0023] Also, α2 is set to 0.50, and α3 is set to 0.3.
By setting it to 0, the value of (1+α3)/(1+α2) becomes 0.
．． 867, and as shown in Fig. 2, the gear difference from 4th speed to 5th speed and from 5th speed to 6th speed is 0.133 and 0.1.
45, the difference between the gears in the overdrive state becomes an appropriate value, making it possible to shift to the overdrive state and smoothly shift gears in the overdrive state.

Next, a second embodiment will be explained. FIG. 3 is a diagram illustrating the second embodiment. In this embodiment, the input shaft N is
The input shaft N is intermittably connected to the second sun gear S2 via a first clutch C1, and the input shaft N is connected to the first sun gear S1 via a fourth clutch C4 arranged in parallel with the first clutch C1. At the same time, the input shaft N is connected via a third clutch C3 arranged in parallel with the first clutch C1.
is intermittably connected to the first ring gear R1, and further connected to the second planet carrier PC2 via the first ring gear R1. Further, the first planet carrier PC1 is connected to the second ring gear R2 and the third ring gear R3 in an intermittent manner via the second clutch C2 or the first one-way clutch WC1.

The other configurations are the same as the first embodiment, and by selectively operating the brakes B1, B2, clutches C1 to C5, and one-way clutches WC1 to WC3 in the combination shown in FIG. 4(a), Six forward speeds and one reverse speed shown in FIG. 4(b) can be obtained.

In this case, as in the first embodiment, the fifth and sixth speeds can be set to overdrive. Next, a third embodiment will be described. FIG. 5 is a diagram illustrating the third embodiment.

This embodiment has the same structure as the first embodiment except that the third ring gear and the third sun gear are connected in an intermittent manner via a sixth clutch. In this case as well, by selectively operating each brake B1, B2, clutches C1-6, and one-way clutches WC1-3 in the combination shown in FIG. 6, nine forward speeds and one reverse speed shown in FIG. 7 can be obtained. Can be done.

In this embodiment, the 7th to 9th speeds are in the overdrive state, and it is possible to obtain three speed ratios in the overdrive state. As described above, by adding a set of simple planetary gear mechanisms to increase the number of gears, a gear ratio more suitable for responding to continuous speed changes of the vehicle can be obtained, and the gear ratio is smaller than 1. It becomes possible to set a plurality of gear stages in the overdrive state, such as 2 to 3 stages.

By setting a plurality of overdrive gears, it is possible to select a gear position that emphasizes the fuel consumption rate during steady driving at relatively high speeds. A reduction in consumption can be expected.

[0030]

[Effects of the Invention] As explained above, the automatic idler gear train of the present invention is capable of responding to continuous speed changes of a vehicle by adding a set of simple planetary gear mechanisms to increase the number of gears. In addition to obtaining a more appropriate gear ratio, by making it possible to set multiple overdrive gears (2 to 3), it is possible to select a gear position that emphasizes fuel consumption during steady driving at relatively high speeds. The engine speed can be precisely controlled and fuel consumption can be expected to be reduced.

[0031] Also, the gear ratio of the speed increasing stage planetary gear is set to 0.45.
and set the gear ratio of the additional planetary gear to less than 0.4, and (1+gear ratio of the additional planetary gear)/(1+
By suppressing the gear ratio (gear ratio of the speed increasing planetary gear) to less than 0.9, it is possible to shift to an overdrive state and smoothly change gears in the overdrive state.

[Brief explanation of the drawing]

FIG. 1 is a schematic diagram showing a planetary gear train of an automatic transmission according to a first embodiment.

FIG. 2 is a chart showing combinations of operating elements of a planetary gear train of the automatic transmission according to the first embodiment and their gear ratios.

FIG. 3 is a schematic diagram showing a planetary gear train of an automatic transmission according to a second embodiment.

FIG. 4 is a chart showing combinations of operating elements of a planetary gear train of an automatic transmission according to a second embodiment and their gear ratios.

FIG. 5 is a schematic diagram showing a planetary gear train of an automatic transmission according to a third embodiment.

FIG. 6 is a diagram showing a combination of operating elements of a planetary gear train of an automatic transmission according to a third embodiment.

FIG. 7 is a chart showing the speed ratio of the planetary gear train of the automatic transmission according to the third embodiment.

[Explanation of symbols]

N Input shaft U Output shaft BG Double-row planetary gear train G1 First planetary gear mechanism G2 Second planetary gear mechanism (speed-up stage planetary gear) G3
Third planetary gear mechanism (additional planetary gear) S1
1st sun gear R1 1st ring gear PC1 1st planet carrier S2 2nd sun gear R2 2nd ring gear PC2 2nd planet carrier S3 3rd sun gear R3 3rd ring gear PC3 3rd planet carrier C1 1st clutch C2 2nd clutch C3 3rd clutch C4 4th clutch C5 5th clutch C6 6th clutch B1 1st brake B2 2nd brake WC1 1st one-way clutch WC2 2nd one-way clutch WC3 3rd one-way clutch

Claims (2)

[Claims] Claim 1: A speed increasing planetary gear consisting of a set of simple planetary gear mechanisms and another planetary gear mechanism connected thereto, and by operating the speed increasing planetary gear, an overdrive state is achieved. Adding an additional planetary gear consisting of another set of simple planetary gear mechanisms to the double-row planetary gear train that obtains the speed change stage, so that the input shaft and the planet carrier of the speed increase stage planetary gear can be connected, The planet carrier of the speed-up stage planetary gear and the sun gear of the additional planetary gear can be connected, the ring gear of the speed-up stage planetary gear and the ring gear of the additional planetary gear can be connected, and the planet carrier of the speed-up stage planetary gear and the additional planetary gear can be connected. In a planetary gear train of an automatic transmission in which both sun gears can be respectively fixed to a stationary part and a planet carrier of an additional planetary gear is connected to an output shaft, the gear ratio of the speed increasing stage planetary gear is changed to an additional planetary gear. A planetary gear train for an automatic transmission characterized by having a gear ratio set larger than that of the gear ratio. 2. The gear ratio of the speed increasing planetary gear is set to be larger than 0.45, the gear ratio of the additional planetary gear is set to less than 0.4, and (1+gear ratio of the additional planetary gear)/(1+increase gear ratio). 2. The planetary gear train for an automatic transmission according to claim 1, wherein the gear ratio of the speed planetary gear is set to less than 0.9.