JPH0238738A - Automatic transmission - Google Patents

Abstract

PURPOSE:To prevent a shaft from being lengthened as well as to contrive to let a device be of fourth forward speed with ease by letting either one of No.1 clutch means or No.2 clutch means connected with an one-way clutch transfer power to a planetary unit via gears, and thereby concurrently letting the power be outputted to an output shaft from a carrier. CONSTITUTION:Power from an input shaft 35 is transferred via a forward clutch 21 or an one-way clutch 30 or directly through a direct clutch 22 by means of selective connection with No.1 and No.2 sun gear 25 and 26, a short and a long pinion gear 27 and 28 and a ring gear 29. In addition, when either of gears is fixed by a brake band 23 and a reverse brake 24, the power is outputted to an output shaft 31 from a carrier 37. This constitution therefore prevents the shaft from being lengthened, thereby enabling change in several parts to let a device be of fourth forward speed from third forward speed with ease at low cost.

Description

DETAILED DESCRIPTION OF THE INVENTION (Objective of the Invention) (Industrial Application Field) The present invention relates to an automatic transmission that can be used in front-wheel drive (FF) and RR (ATM) lance axles.

(Prior Art) In recent years, the power transmission system of automobiles has been shifting from PR to FF due to its advantages such as improved running stability and expanded passenger space.

Figures 3 and 4 show conventionally proposed automatic transmissions, John's 4! This is a system diagram showing a Yatrain. First, to explain about FIG. 3, 1 is an input shaft connected to a torque converter 2, and power is transmitted from the shaft 1 to a planetary gear from either a forward clutch 4 or a direct clutch 3. This power is output from a ring gear 6 and transmitted to a counter gear 7. In the figure, 8 is a brake hand, 9 is a brake, and 10 is a sun gear.

As described above, when shifting to four speeds using the gear train shown in FIG. 3, an overdrive clutch 13 for manually switching the rotational force of the turbine 12 is required in the carrier 11 as shown in FIG. 4.

(Problem to be Solved by the Invention) As described above, the problem with the gear train shown in FIG. 3 is that in order to ensure the automatic function by adding the overdrive clutch 13 as shown in FIG. This means that the shaft length has to be increased. That is,
Since the overdrive clutch 13 is inserted between the ring gear 6 and the carrier 11, the shaft length becomes longer. Therefore, major modifications were required, which caused problems such as increased costs.

Furthermore, in the clutch mechanism of the overdrive clutch 13, it is necessary to configure an oil passage within the input shaft l for supplying hydraulic pressure for turning the clutch on and off during rotation. There were problems such as increase in oil pressure and the need to provide a seal ring to prevent oil pressure leakage. Therefore, it became difficult to share the internal structural parts between FIG. 3 and FIG. 4, and as the size of the input shaft 1 increased, the sun gear IO in FIG.
It was necessary to newly install one of a different size.

The present invention solves problems such as an increase in shaft length, which is a problem with horizontally mounted engines that are generally designed to secure passenger space, and in particular with an increase in the number of gears (3rd to 4th gear). The objective is to provide an automatic transmission that can share many of the parts (transmission case, etc.) used in the three-speed configuration of an aircraft, and can easily be converted to four-speed by changing only a few parts.

[Structure of the invention]

(Means for Solving the Problems) For this reason, the present invention provides power from an input shaft to which driving force is transmitted from a torque converter to either a first clutch means or a second clutch means connected with a one-way clutch. The signal is transmitted to the planetary unit via a gear, and is also output from the carrier of the 8-unit unit to the output shaft.This is a means for solving the problem.

Further, the present invention transmits power from an input shaft to which driving force is transmitted from a torque converter to a planetary unit via a gear using either the first clutch means or the second clutch means, and The torque converter outputs the output from the carrier to the output shaft, and an overdrive brake connected to the second clutch means is disposed between the torque converter and the output shaft. That is.

(Function) The driving force of the input shaft transmitted from the torque converter is the C1 clutch or Ct clutch.

The signal is transmitted from the gear via the ring gear or sun gear to the planetary unit, and is output from the carrier of the unit to the output shaft. In this case, in 3rd gear, the one-way clutch is C! In 4th gear, the overdrive brake acts on the 02 clutch.

(Embodiment) The present invention will be explained below with reference to the embodiments of the drawings. Figs. 1 and 2 show embodiments of the present invention, and Fig.
Figure 2 is 21 in Figure 0 which shows the 4 speed configuration.
is the forward clutch (C1) which is the first clutch means.
Clutch), 22 is a direct clutch (CZ clutch) which is the second clutch means, 23 is a brake band (
B, ), 24 is the reverse brake (B2), 25 is the first
26 is a second sun gear, 27 is a short pinion gear, 28 is a long pinion gear, 29 is a ring gear, 30 is a one-way clutch, 31 is an output shaft, and 32 is a counter gear. Also, Figure 2 is
In addition to eliminating the one-way clutch 30 shown in the figure, a direct clutch 22 disposed between the output shaft 3I and the torque converter 33 and an overdrive brake 34 connected to the first sun gear 25 are provided.

The feature of the present invention is that 3rd and 4th speeds can be easily achieved without changing the shaft length of the automatic transmission. Or direct clutch (CZ
The configuration is such that the signal is transmitted to the planetary unit by one of the clutches 22 and from the output shaft 31 to the counter gear 32 via the carrier 37.

With this configuration, as shown in FIG. 2, by changing the parts of the first sun gear 25 and adding the overdrive brake 34,
It is possible to shift to 4th speed without changing the shaft length. However, in that case, the one-way clutch 30 would have to be abolished, making it difficult to accommodate the shift shock. Note that if the one-way clutch can be abolished, the reverse brake 24 of B2 can be operated with a dog clutch.

Next, the clutch brake operation configuration table for the case shown in Figure 1 is shown in Figure 1.
Table 2 shows a clutch/brake operation configuration table for the case shown in FIG.

Table 1 First, Table 1 will be explained.

(1) In case of reverse R, input shaft 3
The power from 5 passes through a one-way clutch (F) 32 and a direct clutch (Ct clutch) 22, and is applied to a ring gear (R) 29 by a reverse brake (B2) 24.
By fixing the signal, the signal is output to the output shaft 31, and is output to the differential 36 via the counter gear.

(2) In the first driving speed, the power from the input shaft 35 passes through the one-way clutch (F) 30, the first sun gear 25, and the short pinion gear 27.
and reaches the long pinion gear 28, and the brake hand (B
, ) 23, the second sun gear 26 is fixed, so that the output is output from the carrier 37 to the output shaft 3.

(3) In the second driving speed, the power from the input shaft 35 passes through the forward clutch (C, clutch) 21, from the ring gear 29 to the long pinion gear 28, and the second sun gear 26 is fixed by the brake buff F (B+) 23. Since the signal is in contact with each other, it is output from the carrier 37 to the output shaft 31.

(4) In the third driving speed, the power of the input shaft 35 is applied to the C1 clutch 21 and the 02 clutch 22, so the power is transferred to the first sun gear 25 and the short pinion gear 2.
7. The long pinion gear 28, ring gear 29, and second sun gear 26 rotate integrally in the same direction, and the output shaft 31 also rotates integrally for output.

(5) At low L, the C2 crunch 22 is engaged and engine braking is applied. From then on, the same process as in the case of driving first speed is followed.

Table 2 Next, Table 2 will be explained.

(In the case of 11 reverse R, the same operation as in the case of Table 1 except for the one-way clutch F is performed.

(2) At driving I speed, the power from the imbu soto shaft 35 passes through the direct clutch (C2 clutch) 22, the first sun gear 25, the short pinion gear 27 and the long pinion gear 28, and the brake band (B, ) 23. Since the second sun gear 26 is fixed by the carrier 37, the output shaft 3
Output to 1.

(3) In driving 2nd speed, the same operation as in the case of driving 2nd speed in Table 1 is performed.

(4) Driving 3rd gear is also Driving 3 in Table 1.
The operation is exactly the same as the speed.

(5) In the 4th driving speed, the power of the input shaft 35 is transferred to the forward clutch (CI clutch) 2.
1, from ring gear 29 to long pinion gear 28
Since the first sun gear 25 is fixed by the overdrive brake 34, the output is output from the carrier 37 to the output shaft 31.

(6) At low L, C, the clutch 22 is engaged and engine braking is applied. From then on, we will follow the progress of the first driving speed.

〔Effect of the invention〕

Since the present invention is configured as explained in detail above,
This is effective in solving the problem of increasing the shaft length, which is a problem with horizontally mounted engines, and especially increasing the number of gears (3rd to 4th gear). Further, according to the present invention, the number of gears can be increased from 3rd speed to 4th speed with the same shaft length without changing the casing.

That is, since the overdrive brake of the present invention is located between the torque converter and the output shaft, there is no problem of increasing the axial length. Furthermore, according to the present invention, parts used in a 3-speed automatic transmission (for example, a transmission case, etc.)
It is possible to share many speeds, and by changing a few parts, it can be easily converted to 4 speeds, which can greatly contribute to cost reduction.

[Brief Description of the Drawings] Fig. 1 is a system diagram showing a gear train in a 3-speed configuration according to an embodiment of the present invention, Fig. 2 is a system diagram showing a gear train in a 4-speed configuration, Figs. FIG. 4 is a system diagram showing a conventional gear train at 3rd speed and 4th speed, respectively. Explanation of main parts of the diagram 21...Forward clutch (C1 clutch) 22.
- Direct clutch (CZ clutch) 23 - Brake band (B, ) 24 - Reverse brake (8□) 25 - 1st sun gear 26 - 2nd sun gear 27 - Short pinion gear 28 - Long pinion gear 30 - One-way clutch 31 -・Output shaft 33-) Luk converter 34--Overdrive brake 35--Input shaft 37--Carrier b

Claims (2)

[Claims] (1) The power from the input shaft to which the driving force is transmitted from the torque converter is transmitted to the planetary unit via gears by either the first clutch means or the second clutch means connected with the one-way clutch. , an automatic transmission characterized in that output is output from a carrier of the unit to an output shaft. (2) The power from the input shaft to which the driving force is transmitted from the torque converter is transmitted to the planetary unit via the gear by either the first clutch means or the second clutch means, and the carrier of the unit is An automatic transmission characterized in that an overdrive brake is provided between the torque converter and the output shaft and connected to the second clutch means.