JP2007162792A - Flexible flywheel device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent a position of a drive plate for supporting a disc spring from moving in the radial direction and prevent fluctuation of a disc spring load characteristic. <P>SOLUTION: While joining the inner peripheral side of the drive plate 1 to a crankshaft of an engine, the outer peripheral side of the drive plate 1 is joined to the flywheel 3. In the axial direction of the crankshaft, the disc spring 6 is disposed between the drive plate 1 and the flywheel 3, the the outer peripheral side of the disc spring 6 is positioned and supported by a position determining step part 3d of the flywheel 3, the inner peripheral side thereof is supported via a supporting part 1c formed on the drive plate 1, and a recess clearance 7 in which an interval g between the drive plate 1 and the disc spring 6 is a predetermined value or more is formed on the outer peripheral side of the drive plate 1 with respect to the supporting part 1c. The disc spring 6 is constantly supported by the supporting part 1c, and is prevented from being supported on the further outer peripheral side than the supporting part 1c. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a flexible flywheel device in which a flywheel is connected to an engine via an elastic plate for reducing bending vibration and a disc spring, and prevents the load characteristic of the disc spring from fluctuating.

  The internal combustion engine is provided with a flywheel to stabilize the rotation of the crankshaft of the engine, etc., but if the natural frequency of vibration in the bending direction of the crankshaft and the flywheel is in the normal range of the engine, the rotation shaft As a result, bending occurs, and bending vibration is generated, which causes abnormal noise such as a booming sound in the passenger compartment.

  For this reason, for the purpose of reducing bending vibration, an elastic plate is provided between the crankshaft and the flywheel, which has high rigidity in the torsional direction of the rotating shaft and low rigidity in the bending direction. As a result, the natural frequency of the bending vibration of the crankshaft is changed from the normal range of the engine to another range, thereby reducing the generation of abnormal noise.

As a conventional flexible flywheel device in which a mass body such as a flywheel is connected to a crankshaft via an elastic plate, for example, a device described in Patent Document 1 is known. This is because a disc spring is disposed between the elastic plate and the mass body in the axial direction, and one side of the disc spring is contacted with the elastic plate and the other side is in contact with the mass body. It has been made. In other words, a disc spring is arranged between the elastic plate arranged in the axial direction and the mass body, and when the disc spring is bent, friction is generated between the disc spring and the elastic plate / mass body, and bending is caused by frictional resistance. The vibration is damped.
JP 2000-110890 A

  However, there is no sufficient gap between the disc spring and the elastic plate facing the disc spring except for the support portion that supports the inner peripheral side of the disc spring, so that a large axial force is applied to the mass body. When the mass body or the mass body falls, the position of the support portion of the elastic plate that supports the disc spring moves in the radial direction, and the load characteristic of the disc spring differs from the design value. For this reason, the damping action of the bending vibration by the disc spring is not performed stably.

  Accordingly, an object of the present invention is to solve the above problems and to provide a flexible flywheel device in which the position of the support portion of the elastic plate that supports the disc spring does not move in the radial direction.

  According to the first aspect of the present invention, the inner peripheral side of the elastic plate is coupled to the output shaft of the internal combustion engine, while the outer peripheral side of the elastic plate is coupled to the mass body, and in the axial direction of the output shaft, A disc spring is arranged between the mass body, and one side of the disc spring is supported by positioning in the radial direction with the mass body and the other side is formed on the elastic plate. In the flexible flywheel device supported via the support portion, a clearance gap in which the distance between the elastic plate and the disc spring is a predetermined value or more is formed on the one side with respect to the support portion of the elastic plate. It is characterized by that.

  According to the present invention, since the clearance gap of a predetermined value or more is formed between the elastic plate and the disc spring on one side of the inner peripheral side or the outer peripheral side with respect to the support portion of the elastic plate, Even when a large axial force acts or the mass body falls down and the disc spring is compressed, the elastic plate always supports the disc spring, and the portion that supports the disc spring is in the radial direction. Never move to. For this reason, the load characteristic of the disc spring does not change, and the damping action of the bending vibration by the disc spring is stably performed.

  According to a second aspect of the present invention, in the flexible flywheel device according to the first aspect, the clearance gap is narrowed in a direction away from the disc spring as it goes from the support portion to one side. It is formed.

  According to the present invention, the clearance gap is easily formed by drawing the elastic plate.

  The invention according to claim 3 is the flexible flywheel device according to claim 1 or 2, wherein the inner peripheral side of the disc spring is supported by the support portion, and the outer peripheral side of the disc spring is supported by the support portion. An escape clearance is formed.

  According to this invention, the support part of an elastic board supports the inner peripheral side of a disc spring, and the part which supports a disc spring does not move to an outer peripheral side along a radial direction.

  According to a fourth aspect of the present invention, in the flexible flywheel device according to the first or second aspect, the outer peripheral side of the disc spring is supported by the support portion, and the inner peripheral side of the disc spring is supported by the support portion. An escape clearance is formed.

  According to this invention, the support part of an elastic board supports the outer peripheral side of a disc spring, and the part which supports a disc spring does not move to an inner peripheral side along a radial direction.

  According to a fifth aspect of the invention, in the flexible flywheel device according to any one of the first to fourth aspects, the magnitude of the biasing force with respect to the displacement of the disc spring in the mounted state of the disc spring is set to be substantially constant. It is characterized by.

  According to this invention, since the magnitude of the biasing force with respect to the displacement of the disc spring in the mounted state of the disc spring is set to be substantially constant, even when the disc spring is bent and displaced, the change in the biasing force of the disc spring is small. Since the elastic plate has little influence on the axial rigidity, the natural frequency of the bending vibration can be adjusted by paying attention only to the rigidity of the elastic plate, and stable performance can be obtained.

  According to the flexible flywheel device of the present invention, a clearance gap of a predetermined value or more is formed between the elastic plate and the disc spring on one side of the inner peripheral side or the outer peripheral side with respect to the support portion of the elastic plate. Therefore, even if a large axial force acts on the mass body or the mass body falls down and the disc spring is bent and displaced, the elastic plate always supports the disc spring as a support portion. The portion that supports is not moved in the radial direction. For this reason, the load characteristic of the disc spring does not fluctuate, and the damping action of the bending vibration by the disc spring is stably performed.

  In addition, since the magnitude of the urging force with respect to the displacement of the disc spring in the mounted state of the disc spring is set to be substantially constant, even when the disc spring is bent and displaced, there is little change in the urging force of the disc spring, and the elastic plate Since the influence on the rigidity in the axial direction is small, the natural frequency of the bending vibration can be adjusted by paying attention only to the rigidity of the elastic plate, and stable performance can be obtained.

Embodiments of the flexible flywheel device according to the present invention will be described below.
(A) Embodiment 1
First, the first embodiment is shown in FIG. FIG. 1 shows a flexible flywheel device for an engine as an internal combustion engine.

  A projecting portion is formed at an end portion of a crankshaft (not shown) which is an output shaft of an engine (not shown), and a centering hole 1a formed at the center portion of the drive plate 1 as an elastic plate is fitted into the projecting portion, The inner peripheral side of the drive plate 1 is coupled to the end of the crankshaft via a bolt (not shown) inserted through a hole 2a formed in the ring-shaped reinforcing plate 2 and a hole 1b formed in the drive plate 1. Yes. On the other hand, the outer peripheral side of the drive plate 1 is coupled to a flywheel 3 as a mass body. That is, the bolt 5 penetrating the outer peripheral side of the engine control signal plate 4 and the drive plate 1 is screwed into the outer peripheral surface of the flywheel 3.

  A transmission (not shown) is connected to the right side of the flywheel 3 in FIG. 1 via a clutch (not shown). A clutch plate (not shown) is provided on the right side surface of the flywheel 3 in the figure, and a clutch cover (not shown) surrounding the clutch plate is provided. Therefore, a sliding surface 3a that comes into contact with the clutch plate is formed on the inner peripheral side of the flywheel 3, and an attachment surface 3b for attaching the clutch cover is formed on the outer peripheral side of the flywheel 3 via a bolt (not shown). .

  A disc spring 6 for attenuating bending vibration is disposed between the drive plate 1 and the flywheel 3 in the axial direction of the crankshaft. The outer peripheral side of the inner peripheral side and the outer peripheral side of the disc spring 6 is supported by positioning in the radial direction by the flywheel 3. That is, a protrusion 3c that protrudes in the axial direction toward the drive plate 1 is formed along the circumferential direction on the inner peripheral side of the flywheel 3, and the outer periphery of the disc spring 6 is fitted into the protrusion 3c. A positioning step 3d for positioning in the radial direction is formed. As a result, the height from the surface of the flywheel 3 to the positioning step 3d is t / 2 with respect to the thickness t of the flywheel 3. On the other hand, the right end edge in the drawing of the outer peripheral portion of the disc spring 6 is formed with a press-out radius so that the disc spring 6 and the flywheel 3 are not in edge contact.

  On the other hand, the inner peripheral side of the disc spring 6 is supported via a support portion 1 c formed on the drive plate 1. That is, a support portion 1c that protrudes in the axial direction toward the disc spring 6 is formed by narrowing the drive plate 1 in an arc shape, and the flat portion of the end surface on the inner peripheral side of the disc spring 6 contacts the support portion 1c. As a result, the disc spring 6 and the drive plate 1 are prevented from coming into edge contact.

  A clearance gap 7 in which the distance between the drive plate 1 and the disc spring 6 is a predetermined value or more is formed on the outer peripheral side with respect to the support portion 1 c of the drive plate 1. The clearance gap 7 is formed by squeezing the drive plate 1 in the left direction in the figure, which is a direction away from the disc spring 6 as the drive plate 1 moves from the support portion 1c supporting the disc spring 6 toward the outer peripheral side. ing. The predetermined value here means that even when the drive plate 1 is bent or the drive plate 1 is deformed by an input from the axial direction, the contact portion between the drive plate 1 and the disc spring 6 remains on the support portion 1c. The size is such that it does not touch other parts. In the present embodiment, the distance between the drive plate 1 and the disc spring 6 is set to g, and the distance g is substantially the same along the radial direction and the circumferential direction.

  The load characteristic of the disc spring 6 is set to be a flat in which the magnitude of the urging force with respect to the displacement of the deflection of the disc spring 6 in the mounted state of the disc spring 6 is substantially constant.

  Next, the operation of the flexible flywheel device will be described.

  During operation of a vehicle equipped with a flexible flywheel device, a drive plate 1 having a low rigidity in the axial direction and a high rigidity in the rotational direction is interposed between the crankshaft and the flywheel of the engine. By the action of 1, the frequency region where the amplitude of the bending vibration generated between the crankshaft and the flywheel reaches a peak is separated into the crankshaft system and the flywheel system. The natural frequency of the bending vibration between the wheels shifts outside the normal range of the engine, and the bending vibration is reduced. Further, the disc spring 6 is bent between the drive plate 1 and the flywheel 3, whereby the disc spring 6 generates friction between the drive plate 1 and the flywheel 3, and the bending vibration is absorbed and attenuated by the frictional resistance. The

  According to the present invention, the clearance gap 7 is formed between the drive plate 1 and the disc spring 6 on the outer peripheral side with respect to the support portion 1 c of the drive plate 1 provided on the inner peripheral side of the disc spring 6. Therefore, even when a large axial force acts on the flywheel 3 or the flywheel 3 falls down and the disc spring 6 is compressed, the drive plate 1 always supports the disc spring 6 in the support portion 1c. The portion that supports the disc spring does not move to the outer peripheral side along the radial direction. For this reason, the load characteristic of the disc spring 6 does not change, and the damping action of the bending vibration by the disc spring 6 is stably performed.

  According to the present invention, the clearance gap 7 is easily formed by drawing the drive plate 1.

  According to this invention, since the magnitude of the biasing force with respect to the displacement of the disc spring in the mounted state of the disc spring is set to be substantially constant, even when the disc spring is bent and displaced, the change in the biasing force of the disc spring is small. Since the elastic plate has little influence on the axial rigidity, the natural frequency of the bending vibration can be adjusted by paying attention only to the rigidity of the elastic plate, and stable performance can be obtained.

In addition, when the clutch is operated at the time of starting or shifting of the vehicle, heat is generated by sliding between the sliding surface 3a of the flywheel 3 and the clutch plate, and this heat is conducted inside the flywheel 3. The position of the positioning step 3d where the disc spring 6 and the flywheel 3 come in contact is provided on the protruding portion 3c on the opposite side of the sliding surface 3a of the flywheel 3, so that heat is transferred from the disc spring 6. It becomes difficult, and the fluctuation | variation of the load characteristic of the disc spring 6 is suppressed.
(B) Embodiment 2
Next, Embodiment 2 is shown in FIG.

  In this embodiment, contrary to the first embodiment, the inner peripheral side of the disc spring 6 is supported by positioning in the radial direction with the flywheel 3 and the outer peripheral side is supported via a support portion 1 c formed on the drive plate 1. It is intended to support. For this reason, as shown in the figure, the protruding portion 3c and the positioning step portion 3d are formed on the inner peripheral side with respect to the sliding surface 3a of the flywheel 3, while the support portion 1c of the drive plate 1 is more than in the case of the first embodiment. Is also formed on the outer peripheral side. Thereby, the outer peripheral side of the disc spring 6 is supported by the support part 1c, and the clearance gap 7 is formed in the inner peripheral side of the disc spring 6 with respect to this support part 1c.

  According to the present invention, the support portion 1c of the drive plate 1 supports the outer peripheral side of the disc spring 6, and the portion supporting the disc spring 6 does not move toward the inner peripheral side along the radial direction. For this reason, the load characteristic of the disc spring 6 does not fluctuate, and the damping action of the bending vibration by the disc spring 6 is stably performed.

  Since other configurations and operations are the same as those of the first embodiment, description thereof is omitted.

The block diagram which shows a flexible flywheel apparatus (Embodiment 1). The block diagram which shows a flexible flywheel apparatus (Embodiment 2).

Explanation of symbols

1 ... Drive plate (elastic plate)
1c ... support part 3 ... flywheel (mass body)
3d ... Positioning step 6 ... Disc spring 7 ... Escape gap

Claims (5)

While connecting the inner peripheral side of the elastic plate to the output shaft of the internal combustion engine, the outer peripheral side of the elastic plate is connected to the mass body,
In the axial direction of the output shaft, a disc spring is disposed between the elastic plate and the mass body, and one side of the disc spring is positioned in the radial direction by the mass body. In the flexible flywheel device that supports the other side through a support part formed on the elastic plate,
The flexible flywheel device according to claim 1, wherein a clearance gap between the elastic plate and the disc spring is formed on one side of the support portion of the elastic plate with a predetermined value or more. The flexible flywheel device according to claim 1,
The said escape clearance is formed by restrict | squeezing the said elastic board in the direction which leaves | separates from the said disc spring as it goes to the one side from the said support part, The flexible flywheel apparatus characterized by the above-mentioned. The flexible flywheel device according to claim 1 or 2,
The flexible flywheel device, wherein an inner peripheral side of the disc spring is supported by the support portion, and the clearance gap is formed on the outer peripheral side of the disc spring with respect to the support portion. The flexible flywheel device according to claim 1 or 2,
The flexible flywheel device, wherein an outer peripheral side of the disc spring is supported by the support portion, and the clearance gap is formed on the inner peripheral side of the disc spring with respect to the support portion. In the flexible flywheel apparatus in any one of Claims 1-4,
The flexible flywheel device according to claim 1, wherein a magnitude of a biasing force with respect to the displacement of the disc spring in the mounted state of the disc spring is set to be substantially constant.

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