JPH0719283A - Vibration damping device for torsional damper - Google Patents

Abstract

PURPOSE:To provide a vibration damping device being a torsional damper which is constituted to effect stepped control of generating friction torque according to a twist angle. CONSTITUTION:A torsional damper 3 to drive and intercouple a crank shaft 1 and a torque converter 2 under buffering comprises drive plates 5a and 5b coupled to a crank shaft 1; a driven plate 6 coupled to a torque converter cover 2; and a torsion spring 7. A friction member 8 is fitted in a peripheral oblong hole 6a formed in the driven plate 6, effects frictional engagement with the inner peripheral surfaces, positioned facing an axial direction, of the drive plates 5a and 5b, and provides left and right DELTA1 and DELTA2 in a peripheral direction between the oblong hole 6a and the friction member and a gap 6 on the inner peripheral side in a radial direction. When an inclination angle of the oblong hole 6a with the radius (r) of a central shaft is theta, delta is set so as to establish a formula of delta<(DELTA1+DELTA2) tantheta.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention is used in combination with a torsional damper, which is inserted into a power transmission system of a rotary transmission system, particularly an engine such as an engine with torque fluctuation for the purpose of cushioning,
The present invention relates to a device for damping the vibration of a torsional damper.

[0002]

2. Description of the Related Art A conventional example of a vibration damping device for a torsional damper, which is used together with a torsional damper used to damp rotational vibration to generate friction, is shown in FIG. In this conventional example, a crankshaft 51, which is a first rotating body that is rotated by a prime mover (not shown), and a torque converter 52, which is a second rotating body to which rotation is to be input from the crankshaft 51, are driven while being buffered. It comprises a torsional damper 53 to be coupled and a vibration damping device 54 used together with this torsional damper 53.

The vibration damping device 54 is a driving member (drive plate) 55 which is coupled to the crankshaft 51 at a predetermined distance to form a space for a torsional damper.
a, 55b and a driven member (driven plate) 56 which is coupled to the torque converter 52 and inserted into the space.
And a dry resistance type vibration damping device.
That is, the drive plates 55a and 55b respectively have
As shown in FIG. 6, a window 55c in which a torsion spring 57 is interposed is formed, and as shown in FIG.
A notch 55d is formed which engages the claw 59a of the dish plate 59 which urges the plate 8 in the axial direction. Also,
The driven plate 56 is formed with an elongated hole 56a in the circumferential direction into which the friction member 58 is fitted.

The friction member 58 forms clearances (plays) Δ ₁ and Δ ₂ in the left and right in the elongated hole 56a by the engagement of the claw 59a with the drive plate 55b in the circumferential direction, and in the axial direction. Drive plate 55a,
The inner peripheral surfaces of 55b are frictionally engaged with each other (on the drive plate 55b side, friction engagement is performed via the dish plate 59). At this time, the central axis of the long hole 56a coincides with the radius.

In this conventional example, when the relative rotation angle (torsion angle) between one of the first and second rotating bodies and the friction member 58 is within a predetermined angle range, the first and second rotating bodies are used. No friction is generated between them, and a predetermined friction is generated after the relative rotation is performed until _{one of} the gaps Δ ₁ and Δ ₂ becomes 0.

[0006]

However, in the above-mentioned conventional example, when the relative rotation angle between one of the first and second rotating bodies and the friction member reaches a predetermined angle as described above, As shown in FIG. 4 (b), since the structure is such that the friction torque is rapidly generated, the friction torque cannot be finely controlled according to the torsion angle, and the vibration damping effect on the rotation input accompanied by the torque fluctuation can be obtained. As it gets lower
Large noise is generated when friction torque is generated.

An object of the present invention is to provide a vibration damping device for a torsional damper capable of controlling the generated friction torque stepwise according to the torsion angle.

[0008]

To this end, the present invention provides a buffer between a first rotating body rotated by a prime mover and a second rotating body to which rotation is to be input from the first rotating body. A torsional damper drivingly coupled to the lower side, the first damper
A torsional damper having a driving member coupled to the rotating body, a driven member coupled to the second rotating body, and a torsion spring interposed between the two members, and the driven member. A vibration damping device for a torsional damper, comprising: a friction member that is fitted into a circumferentially long hole and frictionally engages with an inner peripheral surface of the drive member that faces in the axial direction. Arranged so that a gap is formed on the left and right in the circumferential direction with respect to the elongated hole, and a gap is also formed on the inner peripheral side in the radial direction, and the central axis of the elongated hole is inclined by a predetermined angle with respect to the radius. It is characterized by being arranged.

[0009]

According to the present invention, when the torsional damper is drivingly coupled to the first rotary body and the second rotary body to which the rotation is to be input, the second rotary body is coupled to the second rotary body. The friction member that is fitted into the circumferential elongated hole provided in the driven member and that frictionally engages with the axially opposed inner peripheral surface of the driving member that is coupled to the first rotating body is It is arranged so as to form a gap on the left and right in the circumferential direction with respect to the elongated hole and also to form a gap on the inner peripheral side in the radial direction, and the central axis of the elongated hole is arranged so as to be inclined at a predetermined angle with respect to the radius. Therefore, for example, when the left and right circumferential gaps between the friction member and the elongated hole are Δ ₁ and Δ ₂ , respectively, and the inclination angle with respect to the radius of the central axis of the elongated hole of the friction member is θ, The gap δ on the radially inner side is set so that δ <(Δ ₁ + Δ ₂ ) tan θ holds. By setting, as shown in FIG. 4 (a), after the relative rotation angle between one of the first and second rotating bodies and the friction member reaches a predetermined angle (± α ₁₁ ), as shown in FIG. Friction torque is generated, and a larger friction torque is generated after the relative rotation angle further increases and reaches a predetermined angle (± α ₁₂ ).
Therefore, the friction torque can be finely controlled according to the torsion angle, the vibration damping effect for the rotation input accompanied by the torque fluctuation is enhanced, and no abnormal noise is generated when the friction torque is generated.

[0010]

Embodiments of the present invention will now be described in detail with reference to the drawings. FIG. 1 is a sectional view in the axial direction showing the configuration of a first embodiment of a vibration damping device for a torsion damper of the present invention, in which 1 denotes a crankshaft which is a first rotating body. The vertical cross section corresponds to a cross section AA in FIG. 2 described later. The crankshaft 1 is a first rotating body that is rotated by a prime mover (not shown).
Is input to the torque converter 2, which is the second rotating body. The crankshaft 1 and the torque converter 2 are drive-coupled to each other by a torsional damper 3 in a buffered manner, and a vibration damping device 4 is used together with the torsional damper 3.

The vibration damping device 4 is a driving member (drive plate) 5a, which is coupled to the crankshaft 1 at a predetermined distance to form a space for a torsional damper.
5b and a driven member (driven plate) 6 which is coupled to the torque converter 2 and inserted into the space,
It is configured as a dry resistance type vibration damping device. That is,
As shown in FIG. 2, each of the drive plates 5a and 5b is formed with a window 5c for interposing a torsion spring 7, and as shown in FIG. 1, a dish plate for axially urging the friction member 8 is pressed. Notch 5 for engaging claw 9a of 9
d is formed. In addition, the driven plate 6,
A circumferential elongated hole (notch) 6a is formed in which the friction member 8 is slidably fitted in the axial direction.

The friction member 8 is shown in FIG.
As shown in FIG.
₁ and Δ ₂ are formed, a gap (play) δ is also formed on the radially inner side, and the central axis of the elongated hole 6a forms an inclination angle θ with respect to the radius r. At this time, the relative rotation angle (torsion angle) between one of the drive plates 5a and 5b connected to the first rotating body and one of the driven plates 6 connected to the second rotating body and the friction member 8 is represented by Δ ₁ , Assuming that α _L and α _R (radian) are associated with Δ ₂ , respectively, it can be expressed by the following equation, as is apparent from FIG.

[Formula 2] Δ ₁ ≈r × α _L , Δ ₂ ≈r × α _R − (1)

## EQU3 ## δ = Δ ₂ × tan θ≈r × α _R × tan θ- (2) In the axial direction, the friction member 8 frictionally engages the inner peripheral surfaces of the drive plates 5a and 5b that face each other. On the drive plate 5b side.
Through frictional engagement).

Next, the operation of the first embodiment will be described.
First, the relative rotation angle (torsion angle) α_L, Α_RIs Δ₁ =
Δ₂ In the relative rotation neutral position where
Almost equal due to the engagement of the claw 9a with the plate 5b
It is designed to be. Therefore, as shown in FIG.
Sea urchin, twist angle α _LAnd α_RWithin a predetermined angle range (-α₁₁
≤ α_L≤ α₁₁, -Α₁₁≤ α_R≤ α₁₁) Is above
As in the conventional example, the friction between the first and second rotating bodies is
Does not occur.

From this stationary state, when relative rotation is performed so that _{one of} the gaps Δ ₁ and Δ ₂ approaches 0, one of α _L and α _R increases and the other decreases depending on the direction of rotation. At this time, as described above, the gaps Δ ₁ and Δ ₂ in the circumferential direction and the gap δ on the inner circumferential side in the radial direction are formed, and the central axis of the elongated hole 56a is inclined by θ with respect to the radius r. Since it is configured, one of the twist angles α _L and α _R exceeds the predetermined angle range (α ₁₁ ≦ | α _L or α _R | ≦
α ₁₂ ), in which case a small friction torque is generated as shown in FIG. Furthermore, the range in which one of the twist angles α _L and α _R is larger than that (| α _L
Alternatively, when α _R | ≧ α ₁₂ ), a large friction torque is generated.

By the way, in order to generate the friction torque stepwise as described above, the following conditional expressions are established on the basis of the above-mentioned Δ ₁ , Δ ₂ , δ, r, and θ of the predetermined angles α ₁₁ , α _12. Need to meet.

## EQU4 ## α ₁₁ = δ / (r × tan θ)-(3)

[Formula 5] α ₁₂ = (Δ ₁ + Δ ₂ ) / r − (4)

Here, since α ₁₁ <α ₁₂ , the characteristics shown in FIG. 4A can be obtained by arranging the constituent elements so as to satisfy the following equation.

[Equation 6] δ <(Δ ₁ + Δ ₂ ) tan θ − (5)

[0017]

As described above, according to the present invention, when the torsional damper is drivingly coupled to the first rotating body and the second rotating body to which the rotation is to be input, the damper is buffered. A friction member is fitted to the inner circumferential surface of the drive member, which is fitted to the driven member that is coupled to the second rotating body, in the circumferential direction, and is axially opposed to the drive member that is coupled to the first rotating body. The mating friction members are arranged so as to form a gap on the left and right in the circumferential direction with respect to the elongated hole, and also to form a gap on the inner peripheral side in the radial direction, and the central axis of the elongated hole forms a predetermined angle with respect to the radius. Therefore, for example, the left and right circumferential gaps between the friction member and the oblong hole are respectively Δ ₁ , Δ ₂ , and the inclination of the central axis of the oblong hole of the friction member with respect to the radius. When the angle is θ, δ <(Δ ₁ + Δ ₂ )
By setting the clearance δ on the radially inner side so that tan θ is established, the relative rotation angle between one of the first and second rotating bodies and the friction member becomes a predetermined angle (± α ₁₁ ). As shown in FIG. 4 (a), a small friction torque is generated after the point of arrival, and a large friction torque is generated after the point of reaching the predetermined angle (± α ₁₂ ) by further increasing the relative rotation angle. To do. Therefore, the friction torque can be finely controlled according to the torsion angle, the vibration damping effect on the rotation input accompanied by the torque fluctuation is enhanced, and no abnormal noise is generated when the friction torque is generated.

[Brief description of drawings]

FIG. 1 is an axial sectional view showing the configuration of a first embodiment of a vibration damping device for a torsional damper according to the present invention.

FIG. 2 is a radial cross-sectional view of the first embodiment.

FIG. 3 is a perspective view of the torsional damper section of the first embodiment.
It is a figure for demonstrating the relative positional relationship of a friction member, a long hole for friction members, and a non-driving member.

FIG. 4A is a diagram for explaining the operation of the first embodiment, and FIG. 4B is a diagram for explaining the operation of the conventional example.

FIG. 5 is a diagram for explaining a conventional technique.

FIG. 6 is a diagram for explaining a conventional technique.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Crank shaft (1st rotating body) 2 Torque converter (2nd rotating body) 3 Torsional damper 4 Vibration damping device 5a, 5b Drive plate (driving member) 6 Driven plate (non-driving member) 7 Torsion spring 8 Friction member 9 Dish plate

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Yoshiro Morimoto 2 Takaracho, Kanagawa-ku, Yokohama, Kanagawa Nissan Motor Co., Ltd.

Claims (2)

[Claims] 1. A first rotating body rotated by a prime mover,
A torsional damper drivingly couples between the second rotary body to which the rotation is to be input from the first rotary body, the drive member being coupled to the first rotary body, and the second rotary body.
A torsional damper having a driven member coupled to the rotating body, and a torsion spring interposed between the two members, and fitted into a circular elongated hole provided in the driven member and A vibration damping device for a torsional damper, comprising: a friction member frictionally engaged with an inner peripheral surface of the drive member facing in the axial direction, wherein a gap is formed in the friction member on the left and right in the circumferential direction with respect to the elongated hole. The vibration of the torsional damper is characterized in that it is arranged so that a gap is also formed on the inner peripheral side in the radial direction, and the central axis of the elongated hole is inclined by a predetermined angle with respect to the radius. Damping device. 2. The left and right circumferential gaps between the friction member and the elongated hole are Δ ₁ and Δ ₂ , respectively, and the radially inner circumferential gap is δ, and the central axis of the elongated hole of the friction member is The vibration damping of the torsional damper according to claim 1, wherein δ is set so that δ <(Δ ₁ + Δ ₂ ) tan θ holds, where θ is an inclination angle with respect to the radius of apparatus.