JPS6283519A - fluid coupling - Google Patents

Abstract

PURPOSE:To prevent generation of noise and an obstruction to performance by extending an engaging arm outward from a turbine runner to arrange the friction connecting means for a pump impeller and a driven shaft on both sides in the shaft direction and providing an inclined face to engage with the engaging arm in the friction engaging arm. CONSTITUTION:An engaging arm 20a is formed in the radial direction of a turbine runner 20 and a couple of clutches 25, 26, whose inclined faces 25b, 26b having a nearly V letter shape are so formed as to be opposed to each other, are arranged on both sides in the shaft direction of said arm 20a, and then the inclined face 20b of the engaging arm 20a is engaged between those clutches. Hereupon the rotational torque of a driving shaft 12 acts upon clutches 25, 26 with a pushing force in the shaft direction by the engaging force components of respective inclined faces 20b, 25b, 26b and is transmitted to a driven shaft 22 but this pushing force increases when a slip is going to increase and an axial thrust force applied to the turbine runner 20 can be reduced nearly to zero. Consequently the generation of a confined sound in a car room and the performance deterioration can be prevented.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a fluid coupling, and more particularly, to a fluid coupling for transmitting rotational torque via fluid between a pump impeller on a drive shaft side and a turbine runner as an example of a driven wheel. Regarding fittings.

(Prior Art) Conventionally, such fluid couplings have been described, for example, in "Automotive Engineering Complete Book 9 Power Transmission Device" (published by Sankaido on November 20, 1981), pages 198 to 216. Since rotational torque is transmitted through fluid, slippage between the driving side and the driven side is unavoidable, and therefore fuel efficiency deteriorates in vehicles using such fluid couplings. In order to solve this problem, JP-A-58-658 discloses a device equipped with a lock-up clutch piston and a pressing means for strongly pressing the lock-up clutch piston toward the converter cover. . This fluid coupling prevents slip loss from occurring between the converter cover and the lock-up clutch piston when the vehicle suddenly accelerates due to the pressing means, and thereby sufficiently maintains the desired performance of the lock-up torque converter. It was designed so that it can be demonstrated effectively.

(Problems to be solved by the invention) However, in such conventional fluid couplings,
-In addition to the hydraulic pressure that acts next, the lock-up clutch piston is firmly pressed against the converter cover by the pressing means as described above, which has the advantages mentioned above, but the lock-up clutch The sliding performance between the piston and the converter cover deteriorates, causing vibrations in the vehicle body when engaging the lock-up clutch or selecting the shift lever, or causing muffled noise in the vehicle interior due to the excitation force caused by the engine piston movement. There was a problem in that it was more likely to occur. Furthermore, when the pressing means presses the lock-up clutch piston toward the converter cover, a thrust force in the axial direction acts on the turbine runner as a reaction, and there is a risk that unreasonable force will be applied and impede the performance of the turbine runner. There was a problem.

(Means for Solving the Problems) Therefore, in order to solve the above-mentioned problems, the present invention provides a pump impeller connected to a drive shaft, and a pump interposed between the pump impeller and the driven wheel through fluid. A fluid coupling comprising: a turbine runner that transmits rotational torque from an impeller to a driven shaft; an engagement arm is formed extending radially outward of the turbine runner; A pair of frictional fastening means are arranged to connect the pump impeller and the driven wheel, and the pair of frictional fastening means are formed with an inclined surface that engages with the engagement arm and is pressed in the axial direction. be.

(Function) According to such a fluid coupling, a pair of frictional fastening means are provided on both sides of the turbine runner in the axial direction, and the frictional fastening force is distributed to the frictional fastening means on both sides, so that the thrust force applied to the turbine runner is reduced. can be made almost zero to prevent the performance from being impaired. Furthermore, the frictional engagement means generates frictional engagement force only by the mechanical engagement action in which the engagement arm of the turbine launch engages with the inclined surface and is pressed in the axial direction. Since no hydraulic force is applied like that of a piston, the frictional engagement means has a higher slipping performance than a conventional lock-up clutch piston, and as mentioned above, when engaging the lock-up clutch or selecting the shift lever, the friction engagement means It is possible to effectively prevent vibrations from being generated or muffled noise in the vehicle interior due to excitation force caused by the piston movement of the engine.

(Example) Embodiments of the present invention will be described below based on the drawings.

1 to 5 are diagrams showing a first embodiment of a fluid coupling according to the present invention.

To explain the mass configuration, in FIG. 1, 1 is an engine, 2 is a manual transmission, 3 is a manual clutch, and a fluid coupling 10 is interposed between the engine 1 and the manual clutch 3. In FIG. 2, 10 is a fluid coupling, and 12 is a drive shaft connected to the crankshaft of the engine on the left side of the figure. A drive plate 14 fixed to the drive shaft 12 is connected to a converter cover 16 via bolts 15, and a pump impeller 18 is integrally formed with the converter cover 16. A turbine runner 20 is disposed between the pump impeller 18 and the converter cover 16 to face the pump impeller 18, and an engaging arm 20a extends radially outward of the turbine runner 20. It is formed. A chamber formed between the pump impeller 18 and the turbine launch 20 is filled with fluid as a rotational torque transmission medium, and this fluid can be used as engine lubricating oil. A torque transmission member 23 whose shaft center portion is spline-coupled with the driven shaft 22 is interposed between the converter cover 16 and the turbine runner 20, and a support parallel to the axis is provided on the outer circumference of the torque transmission member 23. Plate part 23
a is formed. As shown in FIG. 3.4, the turbine runner 20 is fitted inside the support plate portion 23a and supported coaxially with the pump impeller 18.
As shown in the figure, on the outside of the engagement arm 20a, a pair of clutches (frictional engagement means) 25.
26 are fitted and supported. These clutches 25
．． 26 have clutch facings 25a and 2, respectively.
6a is fixed. Further, as shown in FIG. 5, the clutches 25 and 26 are formed with substantially V-shaped inclined surfaces 25b and 26b facing each other, and these inclined surfaces 25 and 26 are formed to face each other.
Slanted surfaces 20b formed at the four corners of the engagement arm 20a are engaged between the engagement arm 20a and the engagement arm 26b. Opening angle θ1 of the inclined surface 25b
is formed to be larger than the opening angle θ2 of the inclined surface 26b (θ, >θ2).

Next, the effect will be explained. Drive shaft 1 from the engine side
The rotational torque transmitted to drive play 1-14,
It is transmitted to the pump impeller 18 via the converter cover 16 and further transmitted to the turbine runner 20 via the fluid. The engagement arm 20 is rotated by the rotation of the turbine runner 20.
The inclined surface 20b of a is engaged with the inclined surface 25b of the clutch 25 and the inclined surface 26b of the clutch 26. The retaining force at this time acts on the pair of clutches 25 and 26 with an axial pressing force, and the clutch facings 25a and 26a are pressed against the pump impeller 18 and the converter cover 16, respectively. As a result, the turbine runner 20, clutch 25.
26, the pump impeller 18 and the converter cover 16 rotate together, and this rotation is further transmitted to the driven shaft 22 via the torque transmission member 23. The rotational torque of the driven shaft 22 is then transmitted to the manual transmission m2 via the manual clutch 3. As mentioned above, the inclined surface 25b of the clutch 25
Since the opening degree θ1 of the clutch 26 is larger than the opening degree θ2 of the inclined surface 26b of the clutch 26, the holding force in the axial direction due to the rotation of the engagement arm 20a is larger in the clutch 25 than in the clutch 26.

This is because not only the engagement force of the engagement arm 20a but also the force acting in the axial direction of the turbine runner 20 due to the fluid is applied to the clutch 26, so the engagement force of the engagement arm 20a acting on the clutch 26 is This is because the pressing forces of both clutches are made substantially equal by making the force smaller than the retaining force acting on the clutches. The pressing force of the clutches 25 and 26 by the engagement arm 20a increases accordingly when the amount of slip of the turbine runner 20 relative to the pump impeller 18 increases, so that the amount of slip remains without increasing as a result, and as compared to conventional The amount of slip can be significantly reduced compared to typical fluid couplings. Furthermore, since a pair of clutches 25, 26 are provided on both sides of the engagement arm 20a of the turbine runner 20 in the axial direction, and the frictional engagement force is distributed to the clutches 25, 26 on both sides, the axial thrust applied to the turbine runner 20 is The force can be reduced to approximately zero to prevent the performance from being impaired. And furthermore, clutch 25.26
The engagement arm 20a of the turbine runner 20 is connected to its inclined surface 25.
b, 26b and is pressed in the axial direction, which mainly generates a frictional fastening force,
Since the clutches 25 and 26 do not primarily apply hydraulic force like the conventional Rosokua Knob clutch piston, they have a higher slipping performance than the conventional lock-up clutch pistons, and when the manual clutch 3 is engaged, the It is possible to effectively prevent vibrations from being generated in the vehicle interior or muffled noise in the vehicle interior due to the excitation force caused by the piston movement of the engine.

In addition, in the first embodiment, the inclined surfaces 25b, 26b
Although the description has been given of a case in which an inclined surface 20b is formed to engage with the engaging arm 20a, instead of the inclined surface 20b, the four corners of the engaging arm 20a may be formed by rounding them at a predetermined radius.

FIG. 6 shows a second embodiment of the present invention.

In the first embodiment, the fluid coupling 10 and the manual transmission 2
In contrast, in this second embodiment, a conventional torque converter with a lock-up clutch device is installed between the fluid coupling 10 and the automatic transmission 2'. The difference is that 30 is inserted. According to the second embodiment, the fluid coupling 10 as shown in FIG. 2 generates vibrations in the vehicle body when the lock-up clutch is engaged or when the shift lever is selected, or vibrations caused by the piston movement of the engine. It is possible to effectively prevent muffled noise in the vehicle interior due to the excitation force.

FIG. 7 shows a third embodiment of the present invention.

In the second embodiment, a fluid coupling 1 is provided between the engine 1 and the torque converter 30 with a rotary clutch device.
In contrast, in this third embodiment, a fluid coupling 10 as shown in FIG. 2 is housed in a fluid coupling 40 with a candle up crunch device, and The difference is that the clutch 26 is disposed in series with the lock-up clutch 126. According to the third embodiment, the structure is more compact than that of the second embodiment, and the same effects as those of the embodiment can be obtained. Although each of the above embodiments has shown a fluid coupling consisting of a pump impeller and a turbine runner as the fluid coupling 10, the fluid coupling 10 is not limited to this, and the fluid coupling 10 may be a torque converter including a stator.

(Effects of the Invention) As described above, according to the present invention, the engaging arm is formed to extend outward from the radius of the turbine runner, and the pump impeller and the driven shaft are arranged on both sides of the engaging arm in the axial direction. A pair of frictional fastening means are arranged to connect the two frictional fastening means, and an inclined surface that engages with the engaging arm and is pressed in the axial direction is formed on the pair of frictional fastening means, so that the sliding performance of the frictional fastening means is allowed to some extent. Therefore, it is possible to effectively prevent vibrations from being generated in the vehicle body when the lock-up clutch is engaged or when the shift lever is selected, or muffled noise in the vehicle interior due to the excitation force caused by the piston movement of the engine.

Further, since the frictional fastening force is generated by distributing it on both sides of the turbine launch, the thrust force applied to the turbine runner can be reduced to almost zero, thereby preventing its performance from being impaired.

[Brief explanation of drawings]

1 to 5 are diagrams showing a first embodiment of the fluid coupling according to the present invention, in which FIG. 1 is a peripheral connection diagram of the fluid coupling 10, FIG. 2 is a sectional view of the fluid coupling 10, and FIG. 3 is a clutch 4 is a sectional view taken along the line IV-IV in FIG. 3, FIG. 5 is a sectional view taken in the direction of the ■ arrow in FIG. 2, and FIG. Peripheral Connection Diagram FIG. 7 is a peripheral connection diagram of the fluid coupling 10 showing the third embodiment. ■...Engine, 2...Manual transmission, 2'...Automatic transmission, 3...Manual clutch, 10...Fluid Coupling, 12... Drive shaft, 14... Drive plate, 15... Bolt, 16... Converter cover, 18... Pump impeller , 20... Turbine runner, 20a... Engaging arm, 20b... Inclined surface, 22... Driven shaft, 23... Torque Transmission member, 23a...Support plate part, 25.26...Clutch (frictional fastening means), 2
5a, 26a... Talatch facing, 25
b, 26b... Slanted surface, 30... Torque converter with Ronqua and Bukuranochi device, 40... Fluid coupling with Rofuku Asop clutch device, 126... Lockup clutch.

Claims (2)

[Claims] (1) A fluid coupling that includes a pump impeller connected to a drive shaft, and a turbine runner that is interposed between the pump impeller and the driven shaft and transmits rotational torque from the pump impeller to the driven shaft via fluid. An engaging arm is formed extending radially outward of the turbine runner, and a pair of frictional fastening means for connecting the pump impeller and the driven shaft are disposed on both sides of the engaging arm in the axial direction, and these A fluid coupling characterized in that a pair of frictional fastening means is formed with an inclined surface that engages with the engagement arm and is pressed in the axial direction. (2) The fluid coupling according to claim 1, wherein the slope angles of the inclined surfaces of the pair of friction means are made different between one friction means and the other friction means.