JP2607395Y2 - Torsion damper - Google Patents

Description

[Detailed description of the invention]

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a torsional damper which is mounted on a crankshaft of a vehicle engine to prevent torsional vibration of the shaft.

[0002]

2. Description of the Related Art In a vehicle engine, resonance of torsional vibration is unavoidable in a normally used rotation range. If the torsional vibration at the time of resonance increases, the flywheel and the crank pulley bolt may become loose, gears may be abnormally worn, and the crankshaft may be fatigued. To absorb the torsional vibration of the crankshaft, a torsional damper that rotates integrally with the crankshaft is attached.

As a torsional damper attached to a vehicle engine, a heat dissipation type damper that adds an inertia ring to a shaft system via an elastic body such as rubber to dissipate vibration energy as heat is used.

Incidentally, the torsional amplitude of the crankshaft shows a peak value at the time of resonance of the crankshaft. However, when a so-called single mass damper having one inertia body is added to the crankshaft, the torsional amplitude of the crankshaft is reduced. The peak is shown in FIG.
As shown by the dashed line above, the image is divided into two parts, and the peak value decreases. Further, having two inertia bodies on the crankshaft,
When a so-called double mass damper is added, one of the peaks formed by splitting in the case of the single mass damper is further split into two, as indicated by the solid line in FIG. The three peaks of the nodes 2 and 3 are formed, and the peak value is further reduced.

[0005] That is, a double mass damper is effective if it is permissible in view of the space for attachment to the crankshaft.

[0006]

However, when a torsional damper is added to the shaft system, the torsional amplitude of the rotating shaft is reduced, and the above-mentioned A section 1, B section 2, and C section 3 are added.
Since the three peak values are almost equal, one of the elastic members constituting the inertia portion of the double mass damper is greatly distorted, and the elastic member having the large distortion becomes severely fatigued. There is a possibility that the durability of the sional damper is impaired. That is, in order to prevent the torsional vibration of the crankshaft, the inertia part having a large natural frequency contributes to the vibration proof in section A, and the inertia part having a small natural frequency contributes to the vibration proof in section C3. I do. Then, both inertia parts contribute to the vibration isolation in Section B2,
The two inertial parts are added to contribute to the vibration proof in Section B2. For this reason, when the amplitude of one inertia part is increased, the amplitude of the other inertia part becomes small, and the fatigue of the inertia part having a large amplitude becomes severe.

Accordingly, the present invention aims to provide a torsional damper having improved durability by making the torsional amplitudes of the two elastic members constituting the two inertial portions of the double mass damper substantially equal. I have.

[0008]

As a technical means for achieving the above object, a torsional damper according to the present invention is provided so as to be connected to a rotating shaft accompanied by torsional vibration, and is integrally formed with the rotating shaft. the damper plate which rotates, 該Da
Extends in the direction intersecting the rotation axis of the damper plate
A first inertial portion formed by attaching a first inertial body via a first elastic body, and a second inertial body formed by attaching a second inertial body via a second elastic body along a surface to be formed. In a torsional damper provided with an inertia portion, the first and second inertia portions have respective moments of inertia of Id ₁ and Id _2, and their natural frequencies are fd ₁ and fd _2. The moment satisfies Id ₁ > Id ₂ and the natural frequency is fd ₁
When <fd ₂ is satisfied, the natural frequency ratio is fd ₂ / fd ₁ , the natural frequency ratio is fd ₂ / fd ₁ = 1.6 to 1.8, and the first inertial body is The distortion shape of the first elastic body when attached to the surface of the damper plate and the second shape when attaching the second inertial body to the surface of the damper plate
It is characterized in that the distortion shape of the elastic body is substantially the same.

[0009]

When the crankshaft rotates, the first elastic body and the second elastic body of the first inertial portion and the second inertial portion are bent, and absorb the torsional vibration of the crankshaft. When the natural frequency ratio fd ₂ / fd ₁ falls within the range of 1.6 to 1.8, nodes A and B of the first elastic body and the second elastic body,
The torsional amplitudes corresponding to the C node have substantially the same value. Only
Also when the two inertial bodies are attached to the damper plate
The strain shape of the first elastic body and the strain shape of the second elastic body are substantially the same.
So that the torsional amplitude of the two inertial parts
Since the peak values are almost equal and are reduced,
The distortion of the first elastic body and the second elastic body is reduced,
The durability as a damper is improved, and the life is prolonged.

[0010]

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a perspective view of a torsional damper according to the present invention.

FIG. 2 is a cross-sectional view for explaining the structure of the double mass damper, taken along a plane including the rotation center axis O. A crankshaft (not shown) rotates about the center axis O. A disk-shaped damper plate 10 is provided at the tip of the crankshaft, at a boss portion such as a pulley (not shown) fitted to the tip of the crankshaft, at an appropriate position on the inner peripheral portion of the damper plate 10. It is fastened by a bolt or the like penetrating the formed through hole 10a. The outer peripheral portion of the damper plate 10 is appropriately bent to form an inclined portion 10b.

A first rubber portion 11 as a first elastic body is attached to the outer side surface of the inclined portion 10b, and a second rubber portion 12 as a second elastic body is attached to the inner side surface. A first inertia ring 13 as a first inertia body is attached to an outer surface of the first rubber portion 11, and the first rubber portion 11 and the first inertia ring 13 form a first inertia portion. . In addition, a second inertia ring 14 as a second inertia body is attached to an outer surface of the second rubber portion 12 to form a second inertia portion. Note that these damper plates 10 and the first
The rubber portion 11, the first inertia ring 13, the second rubber portion 12, and the second inertia ring 14 are a damper plate processed into a predetermined shape.
10 and a first inertia ring 13 and a second inertia ring 14 are placed in a predetermined mold, and vulcanized rubber is poured into the mold to form a first rubber portion.
11 and the second rubber part 12 to the damper plate 10 and the inertia ring 1
It is vulcanized and adhered to 3 and 14 to be formed integrally.

The damper plate 1 of the first rubber portion 11
0 extension of the joint surface 11b of the joining surface 11a and the first inertia ring 13 and the intersection at the point O ₁ on the rotation center axis O,
Joint surface 12a of second rubber portion 12 with damper plate 10
And extension of the joint surface 12b of the second inertia ring 14 so as to intersect at a point O ₂ on the rotation center axis O, there these first rubber portion 11 and the second rubber portion 12 each other via Toibitsu shape.

The first rubber portion 11 and the first inertia ring 13
The moment of inertia of the first inertia portion is represented by Id ₁ , the natural frequency is fd ₁ , the moment of inertia of the second inertia portion comprising the second rubber portion 12 and the second inertia ring 14 is Id ₂ , and the natural frequency is the When fd _2, first inertial portion is formed on the outer surface of the inclined portion 10b of the damper plate 10, the inertial mass and the spring constant is larger than the second inertia unit. That is, Id ₁ > I
d ₂ and fd ₁ <fd ₂ .

The rubber portion of the torsion damper
The shapes, materials and sizes of the inertial rings 11 and 12 and the inertial rings 13 and 14 are appropriately formed, and the ratio fd ₂ / fd ₁ between the natural frequencies of the second inertial portion and the first inertial portion is calculated as fd ₂ / fd. ₁ = 1.6 to 1.8.

The relationship between the frequency of torsional vibration and the torsional amplitude of the shaft system to which the double mass damper is attached will be described with reference to FIGS. In these figures, the one-dot chain line shows the torsional amplitude β ₁ of the first inertial portion, the two-dot chain line shows the torsional amplitude β ₂ of the second inertial portion, and the solid line shows the torsional amplitude βc of the crankshaft. The torsional amplitude βc of the crankshaft has three peaks of A section 1, B section 2 and C section 3 because a torsion damper of double mass is added. FIG.
To 5, as a constant natural frequency fd ₁ of the first inertial unit, it indicates the amplitude at the time of changing a natural frequency fd ₂ of the second inertia unit, in a low frequency range, the first inertial portion Shows a peak at a portion corresponding to the node A due to resonance with torsional vibration. In the high frequency range, the second inertia portion resonates with the torsional vibration and shows a peak at a portion corresponding to the C node 3. Further, in the portion corresponding to B-section 2, both the first inertia portion and the second inertia portion act, and both torsional amplitudes β ₁ and β ₂ show peaks corresponding to the peak of B-section 2. ing.

FIGS. 3, 4 and 5 show the case where the natural frequency fd ₂ of the second inertial body is increased in the order of FIGS.
As shown in FIG. 3, the natural frequency fd ₂ of the second inertial body is small.
In this case, the portion contributing to section B becomes smaller,
The peak value of the torsional amplitude β ₁ of the first inertial portion corresponding to the node 1 and the peak value of the torsional amplitude β ₂ of the second inertial portion corresponding to the C node 3 increase. Also, as shown in FIG. 5, when the natural frequency fd ₂ of the second inertia portion is large , the peaks of the torsional amplitudes β ₁ and β ₂ of the first inertia portion and the second inertia portion corresponding to the B section 2 are obtained. The value is the torsional amplitude β ₁ corresponding to A section 1 and C section 3,
β is larger than the _second peak value.

FIG. 1 is a diagram showing the relationship between the natural frequency ratio fd ₂ / fd ₁ and the peak value α of the torsional amplitude of the damper of any of the first inertia portion and the second inertia portion. Is a graph of data obtained by repeating the experiment while changing the natural frequency fd ₂ of FIG. As described above, when the natural frequency fd ₂ of the second inertia portion increases, the peak values of the torsional amplitudes β ₁ and β ₂ of the damper in the B-section 2 increase as shown in FIG. 5, and the natural frequency fd ₂ Is included in the upper range R in FIG. When the natural frequency fd ₂ decreases, the peak values of the damper torsional amplitudes β ₁ and β ₂ at nodes A 1 and C 3 increase as shown in FIG.

Assuming that the allowable values of the damper torsional amplitudes β ₁ and β ₂ are α ₀ , the case where the natural frequency ratio fd ₂ / fd ₁ is included in the upper range Q in FIG. The torsional amplitude of the part becomes the smallest. Natural frequency ratio f within this range Q
The range of d ₂ / fd ₁ is 1.6 to 1.8. That is,
If the natural frequency ratio fd ₂ / fd ₁ is set within the range of 1.6 to 1.8, the torsional amplitudes β ₁ and β ₂ of the first inertial portion and the second inertial portion are as shown in FIG. The minimum and A
The peak values corresponding to the sections 1, B 2 and C 3 are almost equal. Therefore, regardless of the value of the frequency of the torsional vibration of the crankshaft, the torsional amplitudes β ₁ and β _{2 of} the first inertial portion and the second inertial portion do not become abnormally large. The first rubber portion 11 and the second rubber portion 12 are distorted at substantially stable torsional amplitudes β ₁ and β ₂ .

When the crankshaft rotates due to the operation of the engine, the torsion damper rotates integrally with the crankshaft, and the first inertial portion and the first inertial portion have the first inertial portion.
The rubber portion 11 and the second rubber portion 12 are appropriately bent to generate heat. This heat absorbs the torsional vibration of the crankshaft, and the heat generated in the rubber parts 11 and 12
It is radiated outside from the surface. At this time, rubber part 1
The distortions 1 and 12 have a substantially minimum peak value even when the rotation speed of the crankshaft changes, and show a uniform and stable peak value. Therefore, only the first rubber portion 11 or only the second rubber portion 12 is provided. No rubber parts 11, 12 without severe fatigue
Even tired equally.

FIG. 6 shows another embodiment of the torsion damper, and is a cross-sectional view cut along a plane including the rotation center axis O. The damper plate 22 is fixed to a boss 21a of a pulley 21 attached to a tip end of a crankshaft (not shown) by a bolt 23 penetrating through a through hole 22a formed in an inner peripheral portion of the disc-shaped damper plate 22. Have been. An outer peripheral portion of the damper plate 22 is appropriately bent to form an inclined portion 22b, and a first rubber portion 24 as a first elastic body is mounted on an outer surface of the inclined portion 22b on the outer peripheral side. A second rubber part 25 as a second elastic body is attached to the inner peripheral side. A first inertia ring 26 as a first inertia body is fixed to an outer surface of the first rubber portion 24, and a second inertia ring 27 as a second inertia body is mounted on an outer surface of the second rubber portion 25. It is fixed. The damper plate 22 and the rubber parts 24 and 25 and the inertia rings 26 and 27 are bonded by vulcanization. Further, the rubber portions 24 and 25 are formed in an equal distortion shape.

The first rubber portion 24 and the first inertia ring 26
And the moment of inertia of the first inertia portion
If d ₁ , the natural frequency is fd ₁ , the moment of inertia of the second inertia portion constituted by the second rubber portion 25 and the second inertia ring 27 is Id ₂ , and the natural frequency is fd ₂ , Id ₁ > Id ₂ , f
d ₁ <fd ₂ . Also, the natural frequency ratio f
d ₂ / fd ₁ is set to fall within the range of 1.6 to 1.8. Therefore, as in the case of the embodiment shown in FIG. 2, the torsional amplitudes β ₁ and β _{2 of} the first inertial part and the second inertial part are equal to those of the nodes A and B.
The peak values are almost equal to those of the sections 2 and 3.

[0023]

As described above, according to the torsion damper according to the present invention, the rotating shaft with torsional vibration has two axes.
By adding a double mass damper having two inertial portions, the peak of the torsional amplitude of the rotating shaft is divided into three to reduce the peak value, and the torsional amplitude peaks of the two inertial portions corresponding to these three peaks are reduced. Are made substantially equal, the degree of fatigue of the first elastic body and the degree of fatigue of the second elastic body constituting each of the two inertia portions become almost equal. In addition, since the peak values of the torsional amplitudes of the two inertial portions become substantially equal and are reduced, the distortion of the first elastic body and the second elastic body is reduced,
The durability as a torsional damper can be improved, and the life can be prolonged.

[Brief description of the drawings]

FIG. 1 is a diagram showing the relationship between the ratio of the natural frequencies of two inertial parts and the peak value of the torsional amplitude of the two inertial parts.

FIG. 2 is a cross-sectional view of the torsion damper according to the embodiment cut along a plane including a rotation axis.

FIG. 3 is a diagram showing the relationship between the frequency of vibration of a rotating shaft accompanied by torsional vibration and the torsional amplitude of each of a first inertial part and a second inertial part, where the natural frequency of the second inertial part is small . In addition, the torsional amplitude of the rotating shaft is also shown.

FIG. 4 is a diagram showing the relationship between the frequency of vibration of the rotating shaft accompanied by torsional vibration and the respective torsional amplitudes of the first inertial portion and the second inertial portion, wherein the natural frequency of the second inertial portion is a preferable value. The case is shown, and the torsional amplitude of the rotating shaft is also shown.

FIG. 5 is a diagram showing the relationship between the frequency of vibration of the rotating shaft accompanied by torsional vibration and the respective torsional amplitudes of the first inertial part and the second inertial part, where the natural frequency of the second inertial part is large . In addition, the torsional amplitude of the rotating shaft is also shown.

FIG. 6 is a cross-sectional view of a torsion damper according to another embodiment, taken along a plane including a rotation axis.

FIG. 7 is a diagram showing a relationship between a frequency of torsional vibration and a torsional amplitude of a crankshaft of a vehicle engine, in which a single mass damper is added to the rotating shaft by a dashed line, and a double mass damper is shown by a solid line. This shows a case in which it is added.

Claims (1)

(57) [Scope of request for utility model registration] 1. A damper plate which is provided in connection with a rotating shaft accompanied by torsional vibration and rotates integrally with the rotating shaft, the damper plate intersecting the rotating shaft of the damper plate.
A first inertial portion configured by attaching a first inertial body via a first elastic body, and a second inertial body attached via a second elastic body , along a surface extending in the opposite direction. The second
In the torsional damper where the inertia unit is arranged, wherein the first inertial portion of each of the inertia moment of the second inertia unit and Id ₁ and Id _2, each of the natural frequencies fd ₁ and f
and d _2, when the moment of inertia satisfies Id _1> Id _2, the natural frequency satisfies fd ₁ <fd _2, the natural frequency ratio fd ₂
/ Fd ₁ and the natural frequency ratio is fd ₂ / fd ₁ = 1.6 to
With a 1.8, the second elastic when mounting the strain shape as the second inertial body of the first elastic member for mounting said first inertia member to a surface of the damper plate to a surface of the damper plate A torsional damper characterized in that the shape of the body is substantially the same as that of the body.