JPH0457906B2 - - Google Patents

Description

Detailed Description of the Invention [Object of the Invention] (Industrial Application Field) The present invention relates to a drive member fixed to a drive shaft, and a driven member disposed coaxially and relatively rotatably on the drive member. , relates to an improvement of a torque fluctuation absorbing device consisting of a hysteresis mechanism, a torque limit mechanism, and a damper mechanism interposed between the driven member and the driving member, and can be incorporated into a flywheel of an automobile or as a damper of a ship. Used for engine vibration absorption.

(Prior art) As a prior art related to the present invention, for example, JP-A-55
-There is one published in No. 20964.

This includes a drive member fixed to the drive shaft, a driven member disposed coaxially and relatively rotatably on the drive member, a hysteresis mechanism, a torque limit mechanism, and a damper mechanism interposed between the driven member and the drive member. This is a torque fluctuation absorbing device that attempts to absorb engine vibrations using a hysteresis mechanism, damper mechanism, or torque limit mechanism.

(Problem to be Solved by the Invention) However, in this prior art, the coil spring that constitutes the damper mechanism has almost no circumferential gap in the windows of the flat plate member that is the driving side member and the driven plate that is the driven side member. Since the relative rotation between the driving member and the driven member is determined only by the amount of compression of the coil spring, a sufficient amount of relative rotation cannot be obtained, and effective damping and absorption of vibrations and resonance points may not be sufficient. Nakatsuta.

The technical object of the present invention is to solve these problems and effectively absorb vibrations by setting the resonance point to a value lower than the normal rotational speed of the engine.

[Structure of the invention]

(Means for Solving the Problems) The measures taken to solve the above problems and achieve the technical problems are as follows: It is to provide a gap in the direction.

(Function) By providing the above-mentioned circumferential gap, the coil spring is not actively compressed by the gap during torque transmission, and relative rotation occurs between the driving side member and the driven side member. After that, the driving side member and the driven side member come into contact with both ends of the coil spring and begin to compress the coil spring. Therefore, the total relative rotation amount θ ₀ is the sum of the air gap amount θ ₁ and the compression amount of the coil spring θ ₂ , and the relationship between the ratio of the output amplitude to the input amplitude and the vibration frequency is expressed by the fourth equation with θ ₁ /θ ₀ as a parameter. The result will be as shown in the figure.

In other words, when θ ₁ /θ ₀ = 0, there is a resonance point near the idle rotation frequency f _E , which is the engine's normal rotation speed, but when θ ₁ /θ ₀ ≧0.3, the resonance point is far below the idle rotation frequency f _E. effective vibration absorption.

(Example) Hereinafter, the present invention will be explained based on examples.

The driving members fixed to the drive shaft 11 of the engine with bolts 12 are a first drive plate 13, an outer ring 14, a second drive plate 16, a pin 18 that fastens these three members 13, 14, and 16, and a pin 18 that connects the outer ring 14. The ring gear 15 to be fitted, the first
It consists of an inner ring 17 fastened to the inner peripheral side of the drive plate 13 with bolts 30. A driven member is disposed on the outer periphery of the inner ring 17 via a ball bearing 19 so as to be coaxial with and rotatable relative to the driving member. This driven member consists of a driven plate 20 into which a bearing 19 is fitted, and a flywheel 21 fastened to this driven plate 20 with bolts 31. The torque limit mechanism consists of friction materials 22, 22, driven disks 23, 23, and a disc spring 24 held between the driven plate 20 and the flywheel 21, and the damper mechanism consists of the driven disk 23 and the first and second drive plates 13. , 16 and each window 23b, 23
Seat 32 with rubber 33 and coil splinter 34 which are seat members fitted to b, 13b, 16b
Consists of. Further, the hysteresis mechanism required during relative rotation between the driving member and the driven member includes a thrust plate 26 having a buffering resin cap 27 that is engaged with the first drive plate 13, and a space between this plate 26 and the driven plate 20. It consists of a friction material 25, a disc spring 28 for urging, and a washer 29.

To explain the damper mechanism in further detail, seat 3
2 has a convex R portion 32 a that contacts the concave R portions 13 a and 16 a of the first and second drive plates 13 and 16 and a concave portion 32 b that receives the convex portion 23 a of the driven disk 23 . A gap of θ ₁ (approximately 0.17 rad) is provided between the driven disk 23 and the seat 32 in the circumferential direction.

In the above configuration, when the torque from the drive shaft 11 is transmitted to the first and second drive plates 13 and 16, it pushes the coil spring 34, but a gap of θ ₁ is provided between the driven disk 23 and the coil spring 34. Therefore, while relative rotation occurs between the drive plates 13, 16 and the flywheel 21, torque is transmitted to the flywheel 21 by the amount of hysteresis of the hysteresis mechanism. When the relative rotation is performed θ ₁ and the seat 32 comes into contact with the driven disk 23 , the coil spring 34 is compressed, and torque is transmitted from the coil spring 34 to the flywheel 21 via the driven disk 23 .
The compression amount θ ₂ of this coil spring 34 is approximately
0.26red, and the total relative rotation amount θ ₀ is approximately 0.43red, so θ ₁ /θ ₀ is approximately 0.4. Since this relative rotation amount is sufficiently wide, the resonance point is considerably lower than the idle rotation frequency _fE , and vibration absorption is sufficiently performed.

〔Effect of the invention〕

Another method to achieve this objective is to extend the entire length of the coil spring. However, according to this, buckling tends to occur, and it becomes necessary to secure a space to accommodate a long coil spring.

In contrast, in the present invention, it is sufficient to simply provide a circumferential gap.

[Brief explanation of the drawing]

FIG. 1 is a plan view of a vibration absorbing device according to the present invention;
FIG. 2 is a sectional view of FIG. 1, FIG. 3 is a characteristic diagram according to the present invention, and FIG. 4 is a diagram of the relationship between amplitude ratio and frequency using θ/θ as a parameter. 13, 14, 16, 17...driving member, 20,
21...Followed member, 32...Seat, 34...Coil spring.

Claims (1)

[Claims] 1. A drive member fixed to a drive shaft, a driven member disposed coaxially and relatively rotatably on the drive member, a hysteresis mechanism, a torque limit mechanism, and a damper mechanism interposed between the driven member and the drive member. In the torque fluctuation absorbing device, a circumferential hollow part is provided in the driving side member or the driven side member that comes into contact with the damper mechanism, and the hollow part is
A torque fluctuation absorbing device characterized in that the resonance point is set to 30% or more of the total rotation amount of the driven member in order to make the resonance point lower than the idle rotation frequency.