JPS59170534A - Torsional vibration absorbing device of change gear - Google Patents

Abstract

PURPOSE:To contrive to achieve high efficiency of torque transmission by a method wherein a torque fluctuation is made absorbable with the sliding of friction plate group during the low speed system gear operation under comparatively violent torque fluctuation condition, and the frictional force of the friction plate group is made increasable correspond to the torque increasing with a thrust generating mechanism. CONSTITUTION:The third speed driven gear 123 is integrally provided on a pipe-shaped shaft 11 which is rotatably and externally engaged with an output power shaft 5, the second speed driven gear 122 and the like are engaged to the pipe-shaped shaft 11 via a bearing 292. The forth speed driven gear 124 and the like are made spline fitting to the output power shaft 5, a torsional vibration absorbing device D is interposed between the gear 124 and the pipe-shaped shaft 11. The device D is composed of the first cam plate 161 which is made spline fitting to a cylinder-shaped extended part 14 of the pipe-shaped shaft 11, the second cam plate 162 which is made spline fitting to an outer cylinder 18, each plural driving and driven friction plate 21, 22, primary and secondary springs 241, 242. The secondary spring 242 is operated according to the relative motion caused by the both cam plates 161, 162, thus, a thrust generating device G which increases the frictional force between both friction plates 21, 22 is composed.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a torsional vibration absorbing device for a transmission used in an automobile or the like.

In an automobile, torque fluctuations occur in the power transmission system, for example, when starting, suddenly accelerating, decelerating, or changing gears. If it is a front-engine front-wheel drive vehicle, the propulsion shaft is long enough, so the torque fluctuations will be absorbed mid-way, but in a front-engine front-wheel drive vehicle,
Since it is not possible to provide a long propulsion shaft, the torque fluctuations are likely to be transmitted to various parts and cause torsional vibrations in the power transmission system.Therefore, in this type of vehicle, it is desirable to absorb the torque fluctuations within the transmission.

SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide a torsional vibration absorbing device that can be compactly installed on a transmission shaft such as an output shaft of a transmission, has a simple structure, and has a large vibration absorption capacity. , a tubular shaft equipped with a low-speed gear is rotatably fitted to a transmission shaft such as an output shaft, and a high-speed gear is spline-coupled, and a step is formed on the output shaft between the tubular shaft and the high-speed gear. a plurality of first and second friction plates, which are formed and spline-coupled to the transmission shaft, and which are sandwiched by the stepped portion and the high-speed gear, and which are alternately superimposed on the cylinder and the outer cylinder surrounding the cylinder; The plates are slidably splined to each other, and this friction plate group is biased against the side surface of the high-speed gear with the elastic force of the spring, and the elasticity of the spring is increased in response to an increase in the transmitted torque of the tubular shaft. The tubular shaft and the outer cylinder are connected via a thrust generating mechanism that increases the force generated.

Hereinafter, one embodiment of the present invention will be described with reference to the drawings. FIG. 1 shows a transmission 1 and its surrounding parts of a front-engine front-wheel drive vehicle with a horizontally mounted engine. ), and its input shaft 2 is connected to the crankshaft 3 of the engine via a starting clutch 4.

The transmission 1 is provided with an output shaft 5 parallel to the input shaft 2, and a final drive gear 6 integrally provided with the output shaft 5 is meshed with a final driven gear 8 of a differential device 7. Ru.

The input shaft 2 is integrally equipped with low-speed 1st and 2nd speed drive gears 9. ．． 92. A reverse drive gear 9R is also provided,
Further, the third speed drive gear 93 of the speed measurement system and the fourth and fifth speed drive gears 94.95 of the high speed system are mounted on needle roller bearings 293.2.
94. 294, and are rotatably supported. These 3rd or 5th speed drive gears 93 +94. 9
5 is selectively connected to the input shaft 2 by switching clutches 10 and 10', and is driven thereby.

A tubular shaft 11 is rotatably supported on the output shaft 5 via a plain bearing 25, and this tubular shaft 11 is provided with 1st and 2nd speed driven gears 121. 122 are needle roller bearings 29, . 29□, and a reverse driven gear 29R is supported via a switching clutch 13. These 1st and 2nd speed driven gears 12. .

122 is the first and second speed drive gears 9□ of the input shaft 2.

92 and the reverse driven gear 12R are in mesh with the reverse drive gear 9R via an idle gear (not shown), and are selectively connected to the tubular shaft 11 by the switching clutch 13 to drive it. There is. tubular shaft 1
1 is also integrally provided with a 3-speed driven gear 123, and this gear 12. is engaged with the third speed drive gear 93. The output shaft 5 further includes 4th and 5th speed driven gears 124. 125 are splines 26°26' respectively
They are connected and fixed by a nut 31.

The drive gears 91-9. The driven gears 121 to 12 are all helical gears for smooth power transmission.

Between the tubular shaft 11 and the 4th speed driven gear 124, the tubular shaft 1
A torsional vibration absorbing device of the present invention is provided to connect between the output shaft 1 and the output shaft 5. This torsional vibration absorbing device will be explained next.

A cylindrical extension 14 is formed on the tubular shaft 11 and extends in the axial direction adjacent to the third speed driven gear 123 . A spline 15 is formed on the inner surface of the cylindrical extension 14, and a first cam plate 161 is slidably engaged with the spline 15. A stepped portion 5a is formed on the output shaft 5 at an intermediate position between the tubular shaft 11 and the 4th speed driven gear 124 (in the illustrated example, close to the 3rd speed driven gear 123).
The inner cylinder 17, which is held between the high-speed driven gear 124 and the 4-speed driven gear 124, is connected to the output shaft 5 via a spline 26, similarly to the 4th speed driven gear 124. An outer cylinder 18 surrounding the inner cylinder 17 is arranged adjacent to the extension part 14.

6- Splines 19.20 are formed on the outer circumferential surface of the inner cylinder 17 and the inner circumferential surface of the outer cylinder 18, respectively, and each of the splines 19.20 is provided with a plurality of driving friction plates which are alternately superposed. 21 and driven friction plates 22 are slidably engaged with each other, and between the friction plates 21 and 22 groups and the first cam plate 161 is a second cam plate 16□ that engages with the spline 20 of the outer cylinder 18. are interposed, and these friction plates 21, 22 groups and 4
A pressure receiving plate 23 is interposed between the fast driven gear 124 and the fast driven gear 124 .

A second cam plate 162 is provided between the extension portion 14 and the second cam plate 162.
A primary spring 241 that always presses the cam plate 16□ toward the pressure receiving plate 23 with a constant elastic force is compressed, and a support plate 17α provided at the end of the inner cylinder 17 on the 3rd speed driven gear 123 side First cam plate 16. A secondary spring 242 is interposed between the two. Both of these springs 24+ and 24□ are composed of a plurality of disc springs, but the spring constant of the primary spring 241 is set lower and that of the secondary spring 24□ is set higher.

First and second cam plates 16. ．． 1620, the second
As shown in the figure, a plurality of angle-shaped cams 2γ, 2 are arranged in an annular manner.
8 are integrally protruded, and these are engaged with each other.

From the top of each cam 27, 28, each cam plate 16□,
16□ has a first slope α for positive load transmission and a second slope α for reverse load transmission that descend in opposite directions along the circumferential direction of the square, and as shown in FIG. 3, the first slope α Inclination angle α
is relatively small, and the inclination angle β of the second slope is set to be relatively large.

Also, each slope a, b is connected to each cam plate 16. .

The surfaces α or the second slopes S and B are kept in surface contact with each other.

Thus, the first and second cam plates 16+, 162 have a thrust generating mechanism G that operates the secondary spring 24□ in response to the relative rotation thereof to increase the frictional force between the two friction plates 21, 22. Configure.

Inside the output shaft 5, a tubular shaft 11, a driven gear 12, . 1
Although an oil supply path 30 is provided for lubrication of 22 etc.,
This oil supply path 30 is further extended, and the extension part 14 and the outer cylinder 1
Oil is also supplied to the inside of 8.

Incidentally, the inclination direction of the teeth of the fourth speed gears 94, 124, which are helical gears, is the same as that of the fourth speed gears 94, 12. The gears are selected so that a thrust that presses the driven gear 124 toward the inner cylinder 17 is generated at the meshing portion thereof when the gears are operated.

Next, to explain the operation of this embodiment, normally the elastic force of the primary spring 241 is applied to the second cam plate 16□ and the friction plate 21.2.
Since the second group is pressed against the pressure receiving plate 23, a predetermined frictional force is applied between the driving and driven friction plates 21 and 22, while the secondary spring 24□ is almost in an inactive state. At the first and second cam plates 16, . The cams 27 and 28 of 162 are most deeply engaged with each other as shown in FIG.

Now, assuming that the first speed driven gear 121 is connected to the tubular shaft 11 by operating the switching clutch 13, the rotational torque transmitted from the crankshaft 3 to the input shaft 2 is the same as that of the first speed driven gear 91. It is transmitted to the driving friction plate 21 through the gear 121, the tubular shaft 11, the first cam plate 161, the cam 27°28, the second cam plate 162, and the outer cylinder 18 in this order. The rotational force of the driving friction plate 210 is transmitted to the driven friction plate 22 by the frictional force, and further transmitted to the output shaft 5 via the inner cylinder 17 and further to the differential device 7 via the final drive gear 6.

Even when the second speed driven gear 12□ or the reverse driven gear 12R10- is connected to the tubular shaft 11, the torque of the input shaft 2 is transmitted to the output shaft 5 through a similar path. Also,
When the third speed drive gear 93 is connected to the input shaft 2 by the switching clutch 10, the rotational torque of the input shaft 2 is 3
The signal is transmitted through the speed drive gear 98, the third speed driven gear 123, and the tubular shaft 11 to its extension 14, and thereafter to the output shaft 5 in the same manner as in the case of the first speed.

When the engine is suddenly accelerated during first to third gear or reverse operation, the rotational speed of the input shaft 20 tends to increase, while the output shaft 5 tends to maintain the same speed due to the inertia of the wheels. For this purpose, the tubular shaft 11 and the output shaft 5
There is a difference in rotational speed between the two. As a result, slippage occurs between the driving and driven friction plates 21, 22, and at the same time, the first and second cam plates 16. ．． Relative rotation also occurs between the cams 27 and 1620, and due to the mutual sliding action between the first g+ surfaces α and α of the cams 27 and 28, both cam plates 16□ and 1□ are displaced away from each other, and the first cam plate 16 compresses the secondary spring 24□ to put it into operation.

In this way, the fluctuation of the transmitted energy of the input shaft 2 is reduced by the friction plate 2.
1. Slip between 22 and both cam plates 16□.

This is absorbed by the relative rotation of 16□, and the rotational speed of the output shaft 5 increases smoothly. And both cam plates 161.16
When the secondary spring 24 is actuated by the separation action of □ and its elastic force is increased, the frictional force between the friction plates 21 and 22 is also increased, and the torque of the input shaft 2 is reliably transmitted to the output shaft 5. It becomes like this. During this time, the oil in the transmission case is supplied between the friction plates 21 and 22 via the oil supply path 30, so that the frictional heat generated between each friction plate 21 and 22 can be cooled. can.

On the contrary, when a sudden deceleration operation is performed, the input shaft 2 is driven from the output shaft 5, resulting in a reverse load state. A rotational speed difference in the direction occurs. As a result, a slip occurs between the driving friction plate 21 and the driven friction plate 22, and at the same time, relative rotation occurs between the first and second cam plates 16++ 16□, but in this case, the relative rotation occurs. Since the direction is opposite to that during the acceleration operation, a separation force is applied between the two cam plates 16□ and 16□ due to the mutual sliding action of the second slopes of the cams 27 and 28, and the driving and driven friction plates The frictional force between 21 and 22 is increased. In this way, the reverse load on the output shaft 5 is buffered and transmitted to the input shaft 2.

By the way, in this embodiment, the first
Since the inclination angle β of the second slopes S and b of the second cam plates 161 and 162 is set larger than the inclination angle α of the first slopes α and α that operate during acceleration operation, when the same torque is applied. Considering that, the separation force between the two 13-cam plates 161 and 162 generated by the mutual sliding action of the first slopes α and α is larger than that of the second slope.
b Both cam plates 161 and 16 generated due to mutual sliding action
The separation force between □ is smaller, and therefore the friction force of the driving and driven friction plates 21 and 22, which is increased by the separation force, becomes smaller during acceleration operation and smaller during deceleration operation, and as a result,
During acceleration operation, the slip between the drive and driven friction plates 21 and 22 is suppressed to the minimum necessary for torsional vibration absorption, and torque transmission is carried out promptly, while during deceleration operation, the slip between the drive and driven friction plates 21 and 22 is suppressed to the minimum necessary for absorbing torsional vibrations. This makes it possible to sufficiently absorb torque fluctuations and obtain a smooth engine braking effect.

Torque fluctuations between the input and output shafts 2 and 5, ie, shift shock, caused by switching of the switching clutch 10 or 13 are also absorbed in the same manner as described above.

4-speed drive gear 9 by switching clutch 10 or 10'
When the 4th or 5th speed drive gear 95 is connected to the input shaft 2, each driven gear 124 or 1
25 and is directly transmitted to the output shaft 5.

Therefore, during such power transmission, the torsional vibration absorber 1
) is not activated. This is because sudden torque fluctuations do not occur in high-speed operating conditions where high-speed gears such as 4th or 5th gear operate.

By the way, 4th gear 94.12. During operation, since these are helical gears, both gears 94
．． 124, the driven gear 124 is connected to the friction plate 21.2.
A thrust pushing toward the second group is generated. In this case, if the torsional vibration absorber is not provided with the inner cylinder 17 that contacts the driven gear 124, the driven gear 124 will be pushed by the thrust and the first. Second cam plate 161.16
Do not engage the cams 27 and 28 of □ more strongly than necessary, or
．． Secondary spring 24. ．． If an excessive pressing force is applied to 24□, the vibration absorption characteristics may be disturbed when the torsion and shearing motion absorbing device is activated next time.

However, in the present invention, since the inner cylinder 17 is provided on the output shaft 5 so as to be sandwiched between the stepped portion 5α and the driven gear 124, the thrust of the driven gear 124 is transmitted through the inner cylinder 17. It is supported by the stepped portion 5α, that is, the output shaft 5, and includes cam plates 161 and 162 and springs 241. 242, therefore, the vibration absorption characteristics of the torsional vibration absorption device will not be disturbed.

As described above, according to the present invention, a tubular shaft equipped with a low-speed gear is rotatably fitted to a transmission shaft such as an output shaft, and a high-speed gear is spline-coupled, and the tubular shaft and the high-speed gear are connected together. A stepped portion is formed on the output shaft between the steps, and the stepped portion and an inner cylinder clamped by the high-speed gear are spline-coupled to the transmission shaft, and the inner cylinder and the outer cylinder surrounding it are alternately overlapped. A plurality of first and second friction plates are each spline-engaged with the sliding opening 16, and the friction plate group is biased against the side surface of the high-speed gear with the elastic force of a spring, and the tubular Since the tubular shaft and the outer cylinder are connected through a thrust generating mechanism that increases the elastic force of the spring in accordance with an increase in the transmission torque of the shaft, it is possible to connect the tubular shaft and the outer cylinder when operating a low-speed gear where torque fluctuations are relatively rapid. Torque fluctuations can be effectively absorbed by the sliding of both friction plates to prevent torsional vibration of the transmission shaft, and the frictional force of both friction plates is increased by the thrust generation mechanism as the transmitted torque increases. After buffering, torque transmission can be performed efficiently and reliably.

In addition, even though the friction plate is relatively small, it has excellent vibration absorbing ability, and since the thrust generating mechanism that adjusts the frictional force requires only a small amount of operation, a torsional vibration absorbing device with a large vibration absorbing capacity can be compactly constructed on the transmission shaft. be able to.

-17- Furthermore, since the high-speed gear is disposed adjacent to the friction plate group and is also used as a pressure-receiving member that supports them, it contributes to making the torsional vibration absorbing device more compact and simplifying its structure. be able to. Moreover, when a helical gear is used as a high-speed gear, even if thrust toward the friction plate side occurs during the operation of the high-speed gear, this thrust is supported by the stepped portion of the transmission shaft via the inner cylinder. I made it so that
It is possible to prevent the vibration absorption characteristics of the torsional vibration absorber from changing due to the influence of the thrust of high-speed gears.In other words, it is possible to use helical gears as high-speed gears, and smooth high-speed transmission. It can be carried out.

[Brief explanation of the drawing]

Fig. 1 is a longitudinal sectional plan view of a transmission equipped with a torsional vibration absorbing device according to an embodiment of the present invention, Fig. 2 is an exploded perspective view of the first and second camshafts of the same device, and Fig. 3 is a -18 - It is a sectional view showing the meshing state of the mountain cams of both cam plates. D... Torsional vibration absorption device, G... Thrust generation mechanism 1... Transmission, 5... Output shaft as a transmission shaft, 5a
. . . Stepped portion, 11. . Tubular shaft, 12. ．． 12□, 12
3゜12R...Low speed gear, 124...High speed gear,
17...Inner cylinder, 18...Outer cylinder, 19.20...Spline, 21...Drive friction plate as second friction plate, 2
2... Driven friction plate as a first friction plate, 24. ...
Primary spring, 242... Secondary spring, 26... Spline Patent applicant Honda Motor Co., Ltd. 19- 176-

Claims (1)

[Claims] A tubular shaft equipped with a low-speed gear is rotatably fitted to a transmission shaft such as an output shaft, and a high-speed gear is spline-coupled.
A stepped portion is formed on the output shaft between these tubular shafts and the high-speed gear, and an inner cylinder held by the stepped portion and the high-speed gear is spline-coupled to the transmission shaft. A plurality of first and second sheets are alternately superposed on the outer cylinder.
The friction plates are slidably engaged with each other by splines, and this group of friction plates is biased against the side surface of the high-speed gear by the elastic force of the spring, and the spring is applied in response to an increase in the transmitted torque of the tubular shaft. A torsional vibration absorbing device for a transmission, wherein the tubular shaft and the outer cylinder are connected via a thrust generating mechanism that increases elastic force.