KR20020044226A - Multi-mass flywheel - Google Patents

Abstract

PURPOSE: A multi-mass flywheel is provided to control the torsional vibration transmitted to an engine, to enlarge the controllable range of torsional vibration, and to effectively control both strong and weak torsional vibrations. CONSTITUTION: A multi-mass flywheel comprises a primary mass(120) fixed on a crank shaft, a drive plate(130) connected with the primary mass by interposing a first elastic unit(125), a secondary mass(140) connected with the drive plate by interposing a slight shock elastic unit(135), and a relative displacement limiting unit installed between the drive plate and the secondary mass. The torsional vibration transmitted to the drive plate is reduced by the slight shock elastic unit. If a shock due to the torsional vibration is excessive, two gears(330,410) rotate relatively and contact with each other. Then, strong vibration is absorbed in the first elastic unit.

Description

Multi-mass flywheel {MULTI-MASS FLYWHEEL}

TECHNICAL FIELD The present invention relates to a multi-mass flywheel, and more particularly, to a multi-mass flywheel that reduces vibration with an appropriate elasticity according to the magnitude of engine torsional vibration.

As is well known, a flywheel is a device mounted on a crankshaft of an engine to absorb torsional vibration due to torque fluctuation of the engine.

The flywheel for the above functions is usually mounted on the crankshaft as a heavy mass rotating plate, so that the torque fluctuations transmitted through the crankshaft are reduced by the flywheel and transmitted to the transmission.

However, when the flywheel is a simple mass, the torsional vibration transmitted through the crankshaft cannot be sufficiently absorbed. Accordingly, by providing the flywheel with elastic means, vibration in the rotational direction due to rapid torque fluctuations of the engine is generated by the elastic means. Attempts have been made to absorb.

As an example of such an attempt, the flywheel is composed of a first mass and a second mass, and the torque of the engine is transmitted to the transmission through the flywheel to the crankshaft through the elastic means between the first and second masses. The engine torque is transmitted to the second mass in a state where the torsional vibration transmitted to the fixed first mass is reduced by the elastic means, and the second mass transfers the transmitted engine torque to the transmission.

However, the dual mass flywheel (DMF) of the simple structure as described above does not sufficiently reduce the torsional vibration caused by the torque variation of the engine, and the difference in rotational displacement between the first mass and the second mass due to the torsional vibration of the engine is large. In this case, the effect is not fully exhibited, and there is a demand for improvement of the dual mass flywheel that is currently attempted.

Accordingly, the present invention provides a multi-mass flywheel capable of more effectively coping with torsional vibrations transmitted from an engine, widening the range of torsional vibrations that can be handled, and effectively coping with both the torsional vibrations being large or small. The purpose.

1 is a block diagram showing the coupling relationship of the components of the multi-mass flywheel of the embodiment of the present invention.

2 is a perspective view of a first mass according to an embodiment of the present invention.

3 is a perspective view of a drive plate according to an embodiment of the present invention.

4 is a partial sectional view of a second mass according to an embodiment of the present invention.

5 is a partial cutaway view of a multi-mass flywheel in accordance with an embodiment of the present invention.

Multi-mass flywheel according to the present invention to achieve the above object,

A first mass fixed to the crankshaft;

A drive plate connected to the first mass through a first elastic means for providing a restoring force when a relative displacement occurs between the first mass and the first mass;

A second mass connected to the drive plate via a micro-elastic means for providing a restoring force when a relative displacement occurs between the drive plate and the drive plate;

It includes.

Relative displacement limiting means for limiting the relative displacement occurring between the drive plate and the second mass between the drive plate and the second mass.

The first mass is formed on a circular plate in a circumferential direction by a spring groove on which the first elastic means is mounted is spaced a predetermined distance from the center of the plate,

The drive plate is formed in a circular shape to be coupled to the first mass body, a spring hole for mounting the first elastic means is formed on the drive plate at the same position as the spring groove of the first mass body, A first gear portion having a gear shape is formed on an inner circumferential surface of the through hole formed in the center portion, and the first gear portion is formed with a first mounting groove having a micro-elastic means recessed to an outer circumferential side to mount the micro-elastic means.

The second mass is formed in a circular shape so as to be coupled to the first mass, and a second gear portion is formed to protrude downward from the center lower portion of the second mass, and the first gear portion is formed in the second gear portion. A second mounting groove for mounting the microscopic elastic means is formed at a position corresponding to the microscopic elastic means mounting groove formed in the groove.

Therefore, the relative displacement limiting means may have a coupling structure formed such that the second gear portion is gear-coupled with a predetermined clearance with the first gear portion of the drive plate.

The first elastic means and the fine elastic means can be a compression coil spring, the elastic modulus of the fine elastic means is set smaller than the elastic modulus of the first elastic means.

Hereinafter, the embodiments of the present invention will be described in detail with reference to the accompanying drawings.

1 is a block diagram showing the coupling relationship between the components of the multi-mass flywheel 100 (MULTI-MASS FLYWHEEL; hereinafter referred to as 'MMF') of the embodiment of the present invention.

As shown in FIG. 1, the MMF 100 according to the embodiment of the present invention is a drive plate connected to the first mass 120 through a first elastic body 120 and a first elastic means, which are largely fixed to the crankshaft. 130, the second mass body 140 is connected to the drive plate 130 via the fine moving elastic means, and connected to the clutch mechanism of the transmission.

The first elastic means 125 has a restoring force when a relative displacement occurs between the first mass body 120 and the drive plate 130 through the first mass body 120 and the drive plate 130. to provide.

The fine moving elastic means 135 provides a restoring force when a relative displacement occurs between the drive plate 130 and the second mass body 140 between the drive plate 130 and the second mass body 140. do.

It is preferable to further include relative displacement limiting means for limiting the relative displacement occurring between the drive plate and the second mass between the drive plate and the second mass.

By controlling the mass of the first mass body 120, the drive plate 130, the second mass body 140 and the elastic force of the first elastic means, fine motion elastic means, various vibration damping actions are possible.

2 is a perspective view of the first mass 120 according to the embodiment of the present invention.

As shown in FIG. 2, the first mass has an outer circumferential surface 220 protruding upward from the circular plate 210 to accommodate other components, and mounts the other components at the center thereof. The hub portion 240 for mounting the MMF of the present invention including the first mass 120 on the crankshaft is formed.

On the plate 210, a spring groove 230 is formed in a circumferential direction at a predetermined distance from the center of the plate 210 so as to mount the first elastic means 125. As an example, FIG. 2 shows that the spring groove 230 is formed at four locations.

The spring groove 230 is formed to a depth that can protrude above the plate 210 when the first elastic means 125 is mounted, the first elastic means 125 is a coil spring of a set modulus of elasticity do.

The outer circumferential surface 232 of the spring groove 230 is formed in an arc shape so that the coil spring position in the spring groove 230 can be changed when the coil spring is compressed.

The hub portion 240 has a mounting hole 250 is formed so that the second mass is inserted in the center thereof, the bolt hole for mounting the first mass 120 to the crankshaft outside the mounting hole 245 is formed at a predetermined position.

3 is a perspective view of a drive plate 130 according to an embodiment of the present invention.

The drive plate 130 is formed in a circular shape to be coupled to the first mass body, and a spring hole on the drive plate 130 to fit the first elastic means 125 in the same position on the first mass body 120. 310 is formed.

A through hole 320 is formed in the center of the drive plate 130, and a gear-shaped first gear part 330 is formed on an inner circumferential surface of the drive plate 130 by the through hole 320.

The first gear unit 330 is formed with a first mounting groove 340 of the micro-elastic means indented to the outer circumferential side so that the micro-elastic means 135 can be mounted.

The fine moving elastic means first mounting groove 340 is formed in the same number as the mounting positions of the fine moving elastic means 135, and in FIG.

It is preferable that the position of the microscopic elastic means first mounting groove 340 is not in the same direction as the spring hole 310 for the strength of the drive plate 130. For example, between the spring holes 310 It is preferable to form in the position of.

The fine motion elastic means 135 may be a coil spring having an elastic modulus set as an example, and the elastic modulus of the fine motion elastic means 135 is set smaller than the elastic modulus of the first elastic means.

When the microscopic elastic means 135 is mounted in the microscopic elastic means first mounting groove 340, the position of the microscopic elastic means 135 may be stabilized when the microscopic elastic means operates during the spring retainer 350.

4 is a partial cross-sectional view of the second mass 140 according to the embodiment of the present invention.

The second mass 140 is formed in a circular shape so as to be coupled to the first mass 120, and a second gear portion 410 is formed to protrude downward from the center lower portion of the second mass 140. .

The second gear part 410 is formed to be coupled with a predetermined clearance with the first gear part 330 of the drive plate 130, the first mounting means of the elastic means formed in the first gear part 330 A second mounting groove (510 of FIG. 5) is formed at the position corresponding to the groove 340 to mount the microscopic elastic means.

Clutch mounting holes 420 are formed on the upper surface of the second mass body 140, and a clutch disk (not shown) contacts circularly inside the clutch mounting hole 420 to provide frictional force. A friction surface 430 that can be generated is formed.

The through hole 440 is formed in the center of the second mass body 140 so that the input shaft of the transmission can be inserted and supported. The bearing 450 supports the input shaft of the rotating transmission and prevents friction from occurring. This is installed.

On the outer circumference of the through hole 440, the through hole 450 is formed so that the bolt can penetrate the bolt to the bolt hole 245 at a position corresponding to the bolt hole 245 of the first mass. Is formed.

FIG. 5 illustrates a multiple embodiment according to an embodiment of the present invention in which the first mass body 120, the drive plate 130, and the second mass body 140 are coupled through a first elastic means 125 and a fine moving elastic means 135. Partial incision plan view of a mass flywheel.

As shown in FIG. 5, the first mass body 120 and the drive plate 130 are coupled to the spring grooves 230 and the spring holes 310 formed therebetween, through the first elastic means 125.

The second mass body 140 is coupled to the upper portion of the drive plate 130, and the first mounting groove 340 and the second mounting groove 510 of the second mass body 140 are fine moving elastic means of the drive plate. It is coupled to the space formed through the microscopic elastic means 135.

The drive plate 130 and the second mass body 140 are coupled to each other so that the gear 330 of the drive plate 130 and the gear of the gear portion 410 of the second mass body 140 are predetermined. The clearance d is formed.

Hereinafter, the operation of the multi-mass flywheel of the embodiment of the present invention configured as described above will be described with reference to FIG. 5.

First, the first mass 120 is inserted into the bolt hole 245 formed in the hub portion 240 is coupled to the crank shaft (not shown).

Therefore, when the crankshaft rotates, the first mass 120 fixedly coupled to the crankshaft rotates accordingly.

The drive plate 130 coupled to the first mass 120 through the first elastic means 125 is rotated by the rotational force of the first mass 120.

The rotational force of the drive plate 130 is transmitted to the gear part 410 of the second mass body 140 via the fine moving elastic means 135, whereby the second mass body 140 is rotated.

At this time, the first elastic means 125 is a strong elastic force, the fine elastic means 135 is a weak elastic force.

Therefore, when torsional vibration of the engine is generated while the multi-mass flywheel 100 coupled as described above is rotated, the torsional vibration is transmitted directly to the first mass 120, and the vibration is transmitted to the drive plate 130. Delivered.

Since the torsional vibration transmitted to the drive plate 130 is transmitted through the fine motion elastic means 135 when transmitted to the second mass body 140, the torsional vibration is absorbed by the buffering action of the fine motion elastic means 135. The impact is reduced.

That is, when torsional vibration occurs, the gear part 330 of the drive plate and the gear part 410 of the second mass body 140 rotate relative to each other by a predetermined displacement so that the shock is absorbed by the microscopic elastic means 135 so that the shock is generated. It is reduced.

By the way, the clearance d formed between the gear part 330 of the said drive plate and the gear part 410 of a 2nd mass body is limited.

Therefore, when the impact due to the torsional vibration is so great that the relative rotation of the two gears 330 and 410 is greater than or equal to the clearance d, the two gears 330 and 410 are relatively rotated by the clearance d so that the two gears are rotated. The parts 330 and 410 come into contact with each other, and in this case, a large vibration that is not absorbed by the fine moving elastic means 135 is absorbed by the first elastic means 125.

Therefore, when the torsional vibration caused by the change of the torque transmitted from the engine occurs, the torsional vibration can be reduced with appropriate elasticity according to the magnitude of the torsional vibration.

In addition, as described above, the relative amount of rotation with the first mass 120 fixedly mounted to the crankshaft and the second mass 140 connected to the first mass via a plurality of elastic means is equal to the clearance ( It is not limited by d), and the first elastic means 125 is adjustable according to the length of the mounting groove 230 and the mounting hole 310.

As described above, the preferred embodiment of the multi-mass flywheel of the present invention has been described, but the present invention is not limited to the above-described embodiment, and can be easily performed by those skilled in the art from the embodiments of the present invention. It includes all changes to the extent deemed to be equivalent and modified.

According to the embodiment of the present invention, the torsional vibration can be reduced by appropriate elasticity according to the magnitude of the torsional vibration transmitted from the engine. Therefore, it is possible to effectively reduce the booming phenomenon generated when noise is transmitted to the room due to the rattle vibration or other vibration generated in the transmission.

In addition, according to the length of the mounting groove and the mounting hole of the first elastic means it is possible to adjust the relative rotation amount that the first mass and the second mass can rotate relative to the characteristics of the vehicle is equipped with the multi-mass flywheel of the present invention. .

Claims (7)

A first mass fixed to the crankshaft; A drive plate connected to the first mass through a first elastic means for providing a restoring force when a relative displacement occurs between the first mass and the first mass; A second mass connected to the drive plate via a micro-elastic means for providing a restoring force when a relative displacement occurs between the drive plate and the drive plate; Multi-mass flywheel comprising a. In claim 1, And a relative displacement limiting means for limiting a relative displacement occurring between the drive plate and the second mass between the drive plate and the second mass. In claim 2, The first mass is formed on a circular plate in a circumferential direction by a spring groove on which the first elastic means is mounted is spaced a predetermined distance from the center of the plate, The drive plate is formed in a circular shape so as to be coupled to the first mass body, a spring hole for mounting the first elastic means is formed on the drive plate at the same position as the spring groove of the first mass body, A first gear portion having a gear shape is formed on an inner circumferential surface of the through hole formed in the center portion, and the first gear portion is formed with a first mounting groove having a micro-elastic means recessed to an outer circumferential side to mount the micro-elastic means. The second mass is formed in a circular shape so as to be coupled to the first mass, and a second gear portion is formed to protrude downward from the center lower portion of the second mass, and the first gear portion is formed in the second gear portion. The multi-mass flywheel, characterized in that the second mounting groove for mounting the micro-elastic means is formed in a position corresponding to the micro-elastic means mounting groove formed in the. In claim 3, The relative displacement limiting means is a multi-mass flywheel, characterized in that the second gear portion is a coupling structure formed so as to gear engagement with a predetermined clearance with the first gear portion of the drive plate. The method according to any one of claims 1 to 4, And the first elastic means and the fine moving elastic means are compression coil springs, and the elastic modulus of the fine elastic means is set smaller than the elastic modulus of the first elastic means. In claim 5, A clutch mounting hole for mounting a clutch mechanism is formed on an outer circumferential side of the upper surface of the second mass, and a friction surface is formed inside the clutch mounting hole to generate a frictional force by contacting the clutch disk in a circular shape. Multi-mass flywheel. In claim 6, The through-hole is formed in the center portion of the second mass so that the input shaft of the transmission can be supported, and the bearing is installed on the inner circumferential surface of the through-hole to support the input shaft of the rotating transmission, so that friction does not occur flywheel.