JPH0590000U - Damper device - Google Patents

Abstract

(57) [Abstract] [Purpose] To reduce the torsional vibration of the crankshaft and to reduce the noise accompanying the vibration. [Structure] The first, second, third and fourth rubber members 7, 8 are attached to a damper plate attached to the crankshaft.
First, second, third and fourth inertial bodies 1 via 9, 10
A damper device 4 in which the first damper A, the second damper B, the third damper C, and the fourth damper D are mounted by mounting the first damper 12, the second damper 13, the third damper 14, and the first damper D, respectively. , The third and fourth dampers A, B, C, and D have inertia moments and natural frequencies Id ₁ , Id ₂ , Id ₃ , Id ₄ , and f, respectively.
Assuming d ₁ , fd ₂ , fd ₃ , and fd ₄ , the moment of inertia is Id ₁ > Id ₂ > Id ₃ > Id ₄ , and the natural frequency is fd ₁ <
The dampers are set to have a relationship of fd ₂ <fd ₃ <fd ₄ .

Description

[Detailed description of the device]

[0001]

[Industrial applications]

 The present invention relates to a damper for preventing torsional vibration applied to a crankshaft of an internal combustion engine, and more particularly to a force mass damper device in which four inertia bodies are arranged on a damper plate via elastic bodies.

[0002]

[Prior Art]

 The crankshaft of an internal combustion engine generates torsional vibration around the centerline of rotation during rotation. In particular, when the resonance frequency at which the torsional vibration of the crankshaft peaks and the rotation speed of the crankshaft are in harmony, resonance with a large torsional deformation occurs, and in the worst case, the crankshaft is damaged.

As a damper device for reducing or dispersing such a peak of torsional vibration, a damper device for converting torsional vibration energy into deformation of an elastic body such as rubber and converting it into heat energy to dissipate it. It has been known.

By the way, the torsional amplitude ratio of the crankshaft shows a peak value as shown by the broken line in FIG. 2 when the crankshaft resonates, but if a well-known single mass or double mass damper device is attached to this, a single-dotted chain line is used. As shown, the peak is divided into two, and in the double, the peak is divided into three as shown by the chain double-dashed line, and the value is reduced. That is, the conventional single or double mass damper device controls the torsional vibration response of the shaft system by changing the torsional vibration characteristics of the crankshaft by selecting the mass of each damper, the spring, and the like.

[0005]

[Problems to be solved by the device]

 By the way, since the damper device is installed in a place where space and heat dissipation are severe, it is a problem to install a damper device that is space-saving and efficient, and noise due to vibration of the crankshaft is a problem. Has become.

[0006]

[Means for Solving the Problems]

 Therefore, in the present invention, the first, second, third, and fourth inertial bodies are attached to the damper plate attached to the crankshaft via the first, second, third, and fourth rubber members, respectively. A damper device comprising a first damper, a second damper, a third damper and a fourth damper, wherein the inertia moment of each of the first, second, third and first dampers is Each Id₁, Id₂, Id₃, Id_FourAnd the natural frequency of each damper is fd₁, Fd₂, Fd₃, Fd_FourAnd the moment of inertia is Id₁> Id₂> Id ₃ > Id_Four, The natural frequency is fd₁<Fd₂<Fd₃<Fd_FourIt was set to be a relationship.

[0007]

[Action]

The inertia moments of the first, second, third and fourth dampers are Id ₁ , Id ₂ , Id ₃ and Id ₄ , respectively, and the natural frequencies of the dampers are fd ₁ , fd ₂ , fd ₃ and f, respectively. When d ₄ is set, the moment of inertia is set to Id ₁ > Id ₂ > Id ₃ > Id ₄ and the natural frequency is set to fd ₁ <fd ₂ <fd ₃ <fd ₄ , so the torsional vibration of the crankshaft Are distributed to the individual dampers, and the torsional vibration of the crankshaft is reduced.

[0008]

【Example】

 Hereinafter, embodiments of the present invention will be described step by step. In FIG. 1, reference numeral 1 indicates a crankshaft, and a crankshaft pulley 2 is attached to an end of the shaft 1 by a bolt 3. A damper plate 5, which is the base of the force mass damper device 4, is fitted into the cylindrical portion 2c formed on the crankshaft pulley 2.

The force mass damper device 4 is composed of a damper plate 5 and four dampers A, B, C and D described later. The damper plate 5 is made of a relatively thin conical metal, and an opening 5a for fitting the cylindrical portion 2c and a bolt 6 for fixing the damper plate 5 to the crankshaft pulley 2 are inserted through the central portion of the damper plate 5. A plurality of through holes 5b are formed.

A first damper A, a second damper B, a third damper C, and a fourth damper D are arranged concentrically in this order from the outside on one side surface at the outer peripheral edge of the damper plate 5. Each of these dampers is an annular first, second, third, and fourth rubber member 7, 8, 9, 10 that is an elastic body, and an annular first member provided on each rubber member. , Second, third, and fourth inertial bodies 11, 12, 13, and 14. The first, second, third, and fourth rubber members 7, 8, 9, 10 and the damper plate 5 and the rubber members 7, 8, 9, 10 and the inertia bodies 11, 12, 13, 14 are crimped, respectively. It is fixed. Then, the force mass damper device 4 rotates integrally with the crankshaft 1 and the torsional vibration applied to the shaft 1 causes deformation of the first, second, third and fourth rubber members 7, 8, 9, 10. It is designed to be absorbed by. Further, a plurality of cooling fins 15 are radially formed on the back surface side 5c of the damper plate 5 provided with the dampers, and the length of the cooling fins 15 extends in the radial direction of the dampers A, B, C, D. The length is approximately the same as the mounting range.

Here, the inertia moment and the natural frequency of the force mass damper device 4 have the following relationships. That is, the inertia moment of the first damper A is Id ₁ , the moment of inertia of the second damper B is Id ₂ , the moment of inertia of the third damper C is Id ₃ , and the moment of inertia of the fourth damper D is Id ₄ . When the natural frequency of the first damper A is fd ₁ , the natural frequency of the second damper B is fd ₂ , the natural frequency of the third damper C is fd ₃ , and the natural frequency of the fourth damper D is fd ₄ , the inertia is The dampers A, B, C, and D are set so that the moment Id ₁ > Id ₂ > Id ₃ > Id ₄ natural frequency fd ₁ <fd ₂ <fd ₃ <fd ₄ .

With such a configuration, the damper device 4 has four different natural frequencies with respect to the torsional vibration of the crankshaft 1. Therefore, the torsional amplitude of the crankshaft 1, that is, the resonance peak, is shown in FIG. , As shown by the solid line in FIG. Further, the first damper A has the inertia moment Id ₁ larger than the inertia moment Id ₄ of the fourth damper D and the natural frequency fd ₁ smaller than fd ₄ , so that the crankshaft 1 shown in FIG. Of the four resonance peaks I, II, III, IV, and V, it is involved in low frequency I and II, the fourth damper D is in the high frequency resonance peaks IV and V, and the second damper B is in the resonance peak. In Sections II and III, the third damper C is involved in the resonance peaks III and IV, and can reduce the resonance peak value of the crankshaft 1, and the noise accompanying the vibration of the crankshaft 1 is reduced.

Further, since the resonance peak is reduced, the vibration rates of the dampers A, B, C, D are also reduced, so that the load on the rubber members 7, 8, 9, 10 is reduced and the rubber members 7, 8 are reduced. , 9 and 10 can be suppressed. Furthermore, since the dampers A, B, and CD are provided on one side surface of the damper plate 5, the expansion of the damper device 4 in the axial direction can be suppressed, and the damper plate 5 is formed by the cooling fins 15 formed on the rear surface side 5c. The contact surface between the rubber and the air is increased, the heat dissipation is improved, the temperature of the rubber members 7, 8, 9, 10 can be reduced, and the durability of each rubber member is improved, and the first, second, third and fourth The risk of the dampers A, B, C, and D separating from the damper plate 5 is reduced.

In the embodiments described below, the same components as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted. In the second embodiment shown in FIG. 3, dampers A, B, C and D are arranged on both side surfaces of a damper plate 5. The first damper A and the third damper C are concentrically adhered to one side surface of the damper plate 5, and the second damper B is attached to the rear surface side 5c of the plate 5 and the rear surface of the first damper A. The fourth damper D is adhered to the rear surface of the third damper C, respectively. The upper portion of the first damper A is largely curved and has a function as a cooling fin. By arranging the dampers on both side surfaces of the damper plate 5 in this manner, the damper device 4 can be obtained in which the expansion of the device in the radial direction is suppressed.

Next, FIG. 4 shows a third embodiment of the present invention. In the damper plate 5'in this embodiment, first concave portions 16 and second concave portions 17 are alternately formed by press working from the outer periphery of the plate toward the inner periphery in a circumferential shape. The first concave portion 16 is located on the outer peripheral side of the plate, and the second concave portion 17 is located inside thereof.

A cylindrical first damper A is provided on the outer periphery of the first recess 16, that is, on the outer peripheral surface of the damper plate 5 ′, and on the inner peripheral surface of the first recess 16 on the back side of the first damper A. The cylindrical second damper B is pressure-bonded, and the peripheral surface of the first concave portion 16 facing the second damper B, that is, the outer peripheral surface of the second concave portion 17 has the inside of the third damper C and the second concave portion 17. The fourth damper D is pressure-bonded to the peripheral surface on the back side of the third damper C, and each damper is arranged so as to be within the width L of the damper plate 5 ′. A peripheral groove 18 is formed on the outer peripheral surface 14a of the inertial body 14 of the fourth damper D, so that the surface area of the inertial body 14 is increased.

According to this structure, since the dampers A, B, C and D are accommodated in the width L of the damper plate 5 ′, the damper device 4 can be accommodated in the axial and radial directions. Can be arranged, and when adjusting the moment of inertia and natural frequency, it is possible to adjust without increasing the outer diameter of the damper device 4. Further, since the fourth damper D is disposed inside the damper plate 5 ′ and acts on the V-node (where the frequency is high) of the resonance peak of the crankshaft 1, the fourth damper D acts on the first and second dampers A and B. Although the temperature rises more easily compared to the damper, the surface area of the peripheral groove 18 is large. Therefore, when compared with the fourth damper of the type configured in the same manner as this embodiment and not provided with the peripheral groove 18, the heat dissipation performance is higher. As a result, the thermal load on the rubber member 10 is suppressed and the durability is improved.

By setting the conditions of the moment of inertia and the natural frequency of each damper in the second and third embodiments to the conditions shown in the first embodiment, the torsional vibration of the crankshaft 1 is reduced to the conventional value. It can be reduced compared to the double mass damper device. Further, in the fourth damper D of the third embodiment, the inertial body 14 is provided with the circumferential groove 18, but the present invention is not limited to this, and the point is that the surface area of the inertial body 14 is large and heat dissipation is improved. Any structure may be used, and for example, it may be convex.

[0019]

[Effect of the device]

 As described above, according to the present invention, the resonance peak of the crankshaft is set by setting the inertia moment and the natural rotation speed of the first, second, third and fourth dampers having different natural frequencies and inertia moments. Since the height of the crankshaft can be suppressed, the noise caused by the vibration of the crankshaft can be reduced.

[Brief description of drawings]

FIG. 1 is a partial cross-sectional view of a force mass damper device according to a first embodiment of the present invention.

FIG. 2 is a characteristic schematic diagram of a vibration mode showing a resonance peak of a crankshaft.

FIG. 3 is a partial cross-sectional view of a force mass damper device according to a second embodiment of the present invention.

FIG. 4 is a partial cross-sectional view of a force mass damper device according to a third embodiment of the present invention.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Crankshaft 5, 5'Damper plate 7 1st elastic body 8 2nd elastic body 9 3rd elastic body 10 4th elastic body 11 1st inertial body 12 2nd inertial body 13 3rd inertial body Body 14 Fourth inertial body A First damper B Second damper C Third damper D Fourth damper

Claims (1)

[Scope of utility model registration request] 1. A damper plate attached to a crankshaft is mounted with first, second, third, and fourth inertia bodies via first, second, third, and fourth rubber members, respectively. A damper device comprising a first damper, a second damper, a third damper, and a fourth damper, wherein the inertia moments of the first, second, third, and fourth dampers are respectively Id ₁ , Id ₂ , Id ₃ , and Id _4, and the natural frequencies of the dampers are fd ₁ , fd ₂ , fd ₃ , and fd ₄ , respectively, the moment of inertia is Id ₁ > Id ₂ > Id ₃ > Id ₄ , the natural frequency And the relationship of fd ₁ <fd ₂ <fd ₃ <fd ₄ are respectively set.