KR20060100044A - Dual mass flywheel embedding with oil ring - Google Patents

Abstract

The present invention relates to a dual mass flywheel incorporating an oil ring for uniform distribution of grease or oil therein. To this end, in the dual mass flywheel consisting of the cover 200 and the driven plate 300 assembled between the first and second flywheels 400 and 100 and the first and second flywheels 400 and 100, the driven plate An oil ring journal portion 340 recessed around one surface of both sides of the 300; An oil ring 330 rotatably seated on the oil ring journal 340; And one-way rotating means for the oil ring 330 to rotate in one direction only on the oil ring journal 340.

Dual, Mass, Flywheel, Grease, Spring, Leakage-Proof, Oil-Ring, Journal

Description

Dual mass flywheel embedding with oil ring}

1 is a perspective view of a conventional dual mass flywheel 10,

FIG. 2 is an exploded perspective view of the dual mass flywheel shown in FIG. 1;

3 is a plan view of the first flywheel 400 assembled with the circumferential spring 500 of the dual mass flywheel shown in FIG.

4 is a plan view of the driven plate 300 is assembled in the same state as in FIG.

5 is a half sectional view of the A-A portion of the driven plate 300 of FIG.

6 is an exploded perspective view of a dual mass flywheel with an oil ring according to the present invention;

7 is an enlarged perspective view of the driven plate 300 of FIG. 6,

FIG. 8 is a half sectional view and a partially enlarged view of a portion B-B of FIG. 7;

FIG. 9 is a plan view of the first flywheel 400, the circumferential spring 500 and the driven plate 300 provided with the oil ring in FIG.

10 is a partially enlarged perspective view of the oil ring 330 illustrated in FIGS. 8 and 9.

<Description of the symbols for the main parts of the drawings>

10: dual mass flywheel, 100: second flywheel,

110: first rivet hole, 120: clutch cover mounting hole,

200: cover, 210: cover fixing part,

300: driven plate, 310: driven plate tail,

320: second rivet hole, 330: oil ring,

332: knurled part, 334: internal tooth,

336: top surface, 338: wire,

340: oil ring journal portion, 400: the first flywheel,

410: stopper, 420: outer flow path,

430: inner flow path, 440: support space,

450: gear, 460: third rivet hole,

470: crankshaft connecting hole, 500: circumferential spring,

510: spring support, 520: first spring,

530: second spring.

The present invention relates to a dual mass flywheel incorporating an oil ring, and more particularly, to a dual mass flywheel incorporating an oil ring for uniformly distributing grease or oil therein.

In general, a clutch is provided between the engine and the transmission inside the vehicle. Such a clutch functions to transmit or block the rotational force of the engine toward the transmission. These clutches are equipped with flywheels to increase the rotational moment of inertia, one of which is a dual mass flywheel (also known as a double mass flywheel).

The influence of the rear end bending vibration of the flywheel is very important not only for the engine rumble noise, but also for the interior noise of the vehicle. Usually from 250 to 400 Hz it will have a big influence on the vibration of the drive shaft as well as the overall vibration of the power engine. Therefore, the dual mass fly wheel is applied to improve the bending vibration at the rear end of the crankshaft.

1 is a perspective view of a conventional dual mass flywheel 10. As shown in FIG. 1, a second flywheel 100 is fitted inside the first flywheel 400 in which the gear 450 is integrally formed on the circumference thereof, and both are assembled by rivets. To this end, a plurality of rivet holes 110 are formed in the inner diameter regions of the first and second flywheels 400 and 100.

FIG. 2 is an exploded perspective view of the dual mass flywheel shown in FIG. 1. As shown in FIG. 2, the inside of the dual mass flywheel 10 is largely composed of a second flywheel 100, a cover 200, a driven plate 300, and a first flywheel 400.

The second flywheel 100 is inserted into the first flywheel 400 and is made of heavy metal to increase the rotational moment of inertia. A plurality of clutch cover mounting holes 120 are formed around the second flywheel 100 to connect with the clutch cover. In addition, a plurality of first rivet holes 110 for riveting are formed in the inner diameter region of the second flywheel 100.

The cover 200 has an annular disk shape, and a pair of cover fixing parts 210 are formed on both sides facing each other. The cover fixing part 210 is manufactured by being recessed through press working. The processed cover fixing part 210 is inserted onto the stopper 410 described later. The outer diameter of the cover 200 is welded integrally with the inner diameter of the first flywheel 400. This is to prevent the grease from flowing out by centrifugal force.

The driven plate 300 has a substantially annular disk shape and is provided at one side of the cover 200. The driven plate tail 310 is formed at both ends facing each other, and the driven plate tail 310 is inserted onto the stopper 410 which will be described later. A plurality of second rivet holes 320 through which rivets are formed are formed in the inner diameter region of the driven plate 300.

The first flywheel 400 has a tooth 450 integrally formed around its outer diameter, and is made of heavy metal to increase the rotational moment of inertia. The support space 440 is annularly recessed on the bottom surface of the first flywheel 450, and a plurality of circumferential springs 500 are inserted into the support space 440. The circumferential spring 500 may move in the circumferential direction while compressing and compressing the elastic force in the support space 440. In addition, a plurality of clutch shaft connecting holes 470 are formed in the bottom center area of the first flywheel 400 for connection with a clutch shaft (not shown).

As shown in FIG. 3, an annular support space 440 is formed in the circumferential region of the bottom of the first flywheel 400 so that the circumferential spring 500 can be inserted and moved. In addition, a pair of stoppers 410 protrude from the support part spaces 440 facing each other. The outer and inner sides of the pair of stoppers 410 are the outer flow path 420 and the inner flow path 430 through which grease or oil can move, respectively. As shown in FIG. 3, eight circumferential springs 500 are arranged in a set of four, each with a pair of stoppers 410. Then, grease or oil is injected into each empty space around the support space 440 and the circumferential spring 500.

The circumferential spring 500 is largely composed of a pair of spring support 510 and a pair of coil springs 520 and 530.

The spring support part 510 is a synthetic resin material, and supports both ends of the pair of coil springs 520 and 530. In addition, the spring support 510 has a size that can move within the support space 440, and a plurality of grease grooves (not given a member number) are formed in the outer diameter to increase friction with the first flywheel 400. It is. As the frictional force is increased in this way, the shock jerk phenomenon that causes an impact while the power system vibrates when the user presses the accelerator is alleviated.

In addition, the pair of coil springs 520, 530 is again a first spring 520 having a relatively large diameter, and a small diameter second spring 530 inserted into the first spring 520, Is done. Therefore, the first and second springs 520 and 530 are connected in parallel between the pair of spring supporting parts 510. This is to obtain maximum elastic force in the narrow space.

4 is a plan view of the driven plate 300 assembled in the same state as in FIG. 3, and FIG. 5 is a half sectional view of an A-A portion of the driven plate 300 in FIG. 2. As shown in FIGS. 4 and 5, the driven plate tail 310 of the driven plate 300 is placed on the stopper 410. Then, when the circumferential spring 500 is compressed to one side by centrifugal force, the driven plate 300 is also slightly rotated by the driven plate tail 310.

The conventional dual mass flywheel 10 having such a configuration is assembled in the following manner. First, after assembling the circumferential spring 500 in the assembly process, grease is introduced while rotating the support space 440. This is because a low friction force is required in the neutral state (idling state) of the gear. Then it is evenly distributed on the outside by centrifugal force. Next, the driven plate 300 and the cover 200 are closed, and the outer periphery of the cover 200 is welded and fixed to the first flywheel 400. Then, it is possible to prevent the grease from leaking to the outside by the centrifugal force.

However, the conventional dual mass flywheel as described above has the following problems. In theory, the injected grease should be uniformly distributed inside the support space 440 by centrifugal force. However, as the high speed rotation and the low speed rotation are repeated, the circumferential spring 500 repeats compression and restoration by centrifugal force. This means that the circumferential spring 500 reciprocates in the annular support space 440.

However, as the circumferential spring 500 reciprocates, a phenomenon in which greases uniformly distributed are collected at a specific position occurs. This grease agglomeration is exacerbated as the flywheel life increases. As a result, at some point, the aggregated grease is caused to flow out through the inner diameter of the cover 200. The outflowing grease penetrates into the adjacent clutches and there is a risk of lowering the friction action of the clutch friction surface.

Therefore, in order to alleviate such agglomeration of grease, in the related art, it is noted that agglomeration of grease occurs mainly around the stopper 410. ) And the inner flow path 430 were formed, respectively. The formation of such flow paths 420 and 430 allows the aggregated grease to move to the opposite side.

However, such a design change is only a very local solution, and the above-mentioned problems of the prior art cannot be completely solved. Therefore, various studies and developments for preventing the outflow of grease are in progress.

Accordingly, the present invention has been made to solve the above problems, an object of the present invention is to provide a uniform distribution of grease present in the dual mass flywheel to the oil ring that can prevent the outflow of grease built-in To provide a dual mass flywheel.

An object of the present invention as described above, the dual mass consisting of the cover 200 and the driven plate 300 assembled between the first, second flywheel (400, 100), and the first, second flywheel (400, 100). In the flywheel,

An oil ring journal portion 340 recessed around one surface of both surfaces of the driven plate 300; And

An oil ring 330 rotatably seated on the oil ring journal 340; It can be achieved by a dual mass flywheel with an oil ring, characterized in that consisting of.

In addition, the oil ring 330 is preferably formed of a metal material or a synthetic resin material.

In addition, the oil ring 330 may be formed of a synthetic resin material and further include a metal wire 338 for increasing rotational inertia therein.

In addition, the radially outer surface of the oil ring 330 preferably forms a knurled knurled portion 332 to increase the flow of grease.

In addition, the oil ring 330 may further include a one-way rotating means for rotating only one direction on the oil ring journal 340.

The one-way rotation means described above may be an internal tooth 334 formed repeatedly around the radially inner surface of the oil ring 330.

In addition, the radial width of the oil ring 330 may be 3 mm ~ 10 mm.

Other objects, specific advantages and novel features of the invention will become more apparent from the following detailed description and the preferred embodiments described in conjunction with the accompanying drawings.

The invention will now be described in detail with reference to the accompanying drawings, in which preferred embodiments are shown. Prior to the description, the same member as in the prior art will be used in the following description.

6 is an exploded perspective view of a dual mass flywheel incorporating an oil ring according to the present invention. As shown in FIG. 6, the second flywheel 100 is fitted inside the first flywheel 400 in which the gear 450 is integrally formed on the circumference thereof, and both are assembled by rivets. To this end, a plurality of first rivet holes 110 are formed in the inner diameter regions of the first and second flywheels 400 and 100.

The interior of the dual mass flywheel 10 is largely composed of a second flywheel 100, a cover 200, a driven plate 300, and a first flywheel 400.

The second flywheel 100 is inserted into the first flywheel 400 and is made of heavy metal (eg, steel) to increase the rotational moment of inertia. A plurality of clutch cover mounting holes 120 are formed around the second flywheel 100 to connect with the clutch cover. In addition, a plurality of first rivet holes 110 for riveting are formed in the inner diameter region of the second flywheel 100.

The cover 200 has an annular disk shape, and a pair of cover fixing parts 210 are formed on both sides facing each other. The cover fixing part 210 is manufactured by being recessed through press working. The processed cover fixing part 210 is inserted onto the stopper 410 described later. The outer diameter of the cover 200 is welded integrally with the inner diameter of the first flywheel 400. This is to prevent the grease from flowing out by centrifugal force.

The driven plate 300 has a substantially annular disk shape and is provided at one side of the cover 200. The driven plate tail 310 is formed at both ends facing each other, and the driven plate tail 310 is inserted onto the stopper 410 which will be described later. In the inner diameter region of the driven plate 300, a plurality of second rivet holes 320 through which rivets pass are formed. Specific shapes of the driven plate 300 will be described with reference to FIGS. 7 and 8.

The first flywheel 400 has a tooth 450 integrally formed around the outer diameter, and is made of heavy metal (eg, steel) to increase the rotational moment of inertia. The support space 440 is annularly recessed on the bottom surface of the first flywheel 450, and a plurality of circumferential springs 500 are inserted into the support space 440. The circumferential spring 500 may move in the circumferential direction while compressing and compressing the elastic force in the support space 440. In addition, a plurality of clutch shaft connecting holes 470 are formed in the bottom center area of the first flywheel 400 for connection with a clutch shaft (not shown).

FIG. 7 is an enlarged perspective view of the driven plate 300 of FIG. 6, and FIG. 8 is a half sectional view and a partially enlarged view of the portion B-B of FIG. 7. As shown in FIGS. 7 and 8, an oil ring journal portion 340 is formed around the circumference of the driven plate 300. The oil ring journal 340 is composed of a smooth vertical plane and a horizontal plane.

And, the oil ring 330 is obtained on this oil ring journal 340 as it is. Thus, the oil ring 330 is rotatable on the oil ring journal 340. However, the oil ring 330 does not fall out because the cover 200 is assembled to the upper surface. An oil film formed by grease is formed between the oil ring 330 and the oil ring journal part 340 to enable smooth lubrication. The detailed shape of the oil ring 330 will be described in detail with reference to FIG. 10.

FIG. 9 is a plan view of the driven plate 300 provided with the first flywheel 400, the circumferential spring 500, and the oil ring 330 in FIG. 6. As shown in FIG. 9, in the fixed state, the oil ring 330 may be relatively rotated in the direction of the arrow (counterclockwise with reference to FIG. 9). This rotation is caused by high frequency vibrations in which the rotational fluctuations of the engine are transmitted to the flywheel. In addition, it is a matter of course that the rotation in the clockwise direction to occur by reversing the shape of the oil ring 330.

10 is a partially enlarged perspective view of the oil ring 330 illustrated in FIGS. 8 and 9. As shown in FIG. 10, the annular oil ring 330 is manufactured by injecting a plastic material, a ceramic, a silicon material, or the like. Inside the oil ring 330, a metal wire 338 is inserted along the circumference. The wire 338 may be manufactured by insert injection, etc., and because the wire 338 is relatively heavy compared to the plastic material to increase the rotational moment of inertia of the oil ring 330. The radial width of this oil ring 330 may be 3 mm to 10 mm. If less than 3 mm, the effect of distributing grease is insignificant, and if more than 10 mm, there may be interference between the rotating oil ring 330 and the fixed cover 200.

On the radially inner surface of the oil ring 330, an internal tooth 334 is regularly arranged along one circumferential direction. The internal tooth 334 rotates while being in contact with the vertical wall of the oil ring journal 340, rather than having a toothed bite. The internal tooth 334 has a right triangle shape or a shape inclined to one side. Therefore, when a fine (rotational) vibration is transmitted to the dual mass flywheel, the oil ring 330 makes relative vibration. At this time, the internal tooth 334 causes the frictional force of the one-way movement and the frictional force of the opposite movement to be different. If this difference persists, the oil ring 330 makes relative rotation. That is, the internal tooth 334 makes a difference in the frictional force generated in the two-way vibration.

The knurling portion 332 is machined on the radially outer surface of the oil ring 330. The knurling portion 332 has an effect of making the surface roughness of the outer surface very rough, so that the adhered grease is easily moved in the circumferential direction. That is, as the oil ring 330 rotates, the grease buried in the knurling portion 332 moves more than when the knurling portion 332 is absent.

Hereinafter, a method of assembling a dual mass flywheel having the above configuration will be described. First, eight circumferential springs 500 are positioned on the first flywheel 400. Then, grease is injected while rotating the first flywheel 400. Then, the grease is filled while filling the empty space inside the support space 440 and the circumferential spring 500 by centrifugal force.

Next, the driven plate 300 shown in FIG. 7 is assembled to the first flywheel 400 so as to be in a state as shown in FIG. 9. At this time, the driven plate tail 310 is placed on the stopper 410. The oil ring 330 is placed on the oil ring journal 340 of the driven plate 300.

Then, the cover 200 is covered, and the circumferential surface of the cover 200 and the inner diameter surface of the first flywheel 400 are welded. Then, after assembling the second flywheel 100, a rivet (not shown) is fastened so as to pass through the first, second, and third rivet holes 110, 320, and 460 in common. Through this process, the assembly of the dual mass flywheel according to the present invention is completed.

Hereinafter, the operation of the dual mass flywheel assembled as described above will be described in detail. First, as the service life of the dual mass flywheel of the present invention becomes longer, the grease inside the flywheel is agglomerated in part, unlike the state which was shipped from the factory. However, the oil ring 330 is subjected to relative movement (eg, rotational reciprocation) with respect to the driven plate 300 due to the vibration of the fine, continuous and high frequency characteristics applied to the flywheel.

At this time, a difference occurs between the frictional force (friction force between the oiling and oiling journal portions) in one direction of relative rotation and the frictional force (friction force between oiling and oiling journal portions) in the opposite direction of rotation. This is due to the asymmetric internal tooth 334 protruding to the inner wall of the oil ring 330. Due to the large and small difference in frictional force, the oil ring 330 is relatively rotated in a direction in which the frictional force is small. Or more relative rotation in the direction of less friction. As this phenomenon continues, the oil ring 330 rotates in one direction with respect to the driven plate 300.

At this time, grease deposited on the knurling portion 332 moves together. That is, grease is buried in the knurled portion 332 as the oil ring 330 passes through the grease, and the grease is moved to another area and naturally buried in another area. Therefore, the agglomeration of grease is eliminated and a relatively uniform distribution of grease is achieved.

Dual mass flywheel disclosed in the present invention can be variously modified according to the capacity and size, and thus the size and number of oil rings can be modified.

In addition, in the present invention, but the internal tooth as an example of the one-way rotating means, but not necessarily limited to this, various one-way rotating means familiar to those skilled in the art, such as poles and ratchets, toothed type can be applied.

In addition, in the present invention, the oil ring is located on the upper surface of the driven plate 300, but may be located on the lower surface of the driven plate 300, or may be located on both sides of the driven plate 300.

In addition, oil rings and oil ring journals can be replaced by needle bearings.

Therefore, according to the exemplary embodiment of the present invention as described above, the grease existing in the dual mass flywheel may be uniformly distributed to prevent the outflow of the grease.

This means that even if the mass flywheel is used for a long time, it can maintain constant reliability without degrading performance. In addition, since there is no grease leakage to the clutch, it can make a great contribution to the safe operation of the clutch.

Although the present invention has been described in connection with the above-mentioned preferred embodiments, it will be readily apparent to those skilled in the art that various other modifications and variations can be made without departing from the spirit and scope of the invention. It is obvious that all modifications fall within the scope of the appended claims.

Claims (7)

In the dual mass flywheel composed of the first and second flywheels 400 and 100, and the cover 200 and the driven plate 300 assembled between the first and second flywheels 400 and 100, An oil ring journal portion 340 recessed around one surface of both surfaces of the driven plate 300; And An oil ring 330 rotatably seated on the oil ring journal 340; Dual mass flywheel with an oil ring, characterized in that consisting of. The dual mass flywheel with oil ring according to claim 1, wherein the oil ring (330) is formed of a metal material or a synthetic resin material. The dual mass flywheel of claim 1, wherein the oil ring (330) is formed of a synthetic resin material and further includes a metal wire (338) for increasing rotational inertia therein. 2. The dual mass flywheel incorporating an oil ring according to claim 1, wherein the radial outer surface of the oil ring (330) forms a knurled knurled portion (332) to increase the flow of grease. The dual mass flywheel of claim 1, further comprising one-way rotating means for rotating the oil ring (330) in one direction only on the oil ring journal portion (340). 6. The dual mass flywheel with oil rings according to claim 5, wherein the one-way rotation means is an internal tooth 334 formed repeatedly along a circumference of a radially inner surface of the oil ring 330. The dual mass flywheel incorporating an oil ring according to claim 1, wherein the oil ring (330) has a radial width of 3 mm to 10 mm.

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