JPH0752441Y2 - Flywheel - Google Patents

Description

[Detailed description of the device]

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a flywheel, in particular, a flap connected to a clutch disc on the output side.

[0002]

2. Description of the Related Art For example, a flywheel used for an automobile engine has a central portion fixed to a crankshaft on the engine side and a clutch mounted on the outer peripheral side. Further, on the side surface on the clutch side, a friction surface with which the friction member of the clutch disc is in pressure contact is formed.

In such a flywheel, a split type flywheel has been proposed. The split type flywheel has a first flywheel and a second flywheel, and a damper mechanism is housed between them. The first flywheel and the second flywheel are connected to each other so as to be rotatable relative to each other.

[0004]

In the split type flywheel, a lubricant (grease) sealed type bearing is used as a bearing for supporting the first flywheel and the second flywheel with each other. However, the sealability of this bearing may deteriorate during long-term operation, and the lubricant may leak to the clutch facing side.

When the damper mechanism provided inside the flywheel is a viscous damper mechanism, liquid such as grease is filled. When the liquid leaks out in such a viscous damper mechanism, the liquid passes through the bearing and is scattered to the clutch facing side. As described above, if the lubricant or the like leaks to the clutch facing side and adheres to the friction surface of the flywheel, slippage occurs in the clutch, and in extreme cases, the vehicle may be unable to run. Such problems are not limited to split flywheels,
Even in a normal integrated flywheel, grease and the like applied to the drive shaft on the transmission side scatters, causing the same problem.

An object of the present invention is to provide a flywheel capable of preventing slippage of the clutch.

[0007]

A flywheel according to the present invention comprises a flywheel body and an oil discharge mechanism. The flywheel main body has a friction surface which is connected to the input side rotating body and which can be brought into pressure contact with the friction member of the output side clutch disc. The oil discharge mechanism is formed on the circumference of the flywheel main body in the radial direction at predetermined intervals, and discharges the oil moving on the clutch disc side by the action of centrifugal force to the input side rotating body side of the flywheel main body. A plurality of first through-holes for forming a plurality of first through-holes, and said first through-holes formed in the flywheel main body so as to correspond to the gap portions radially inward of the friction surface and radially outward of the first through-hole forming portion. It is composed of a plurality of second through holes for discharging oil.

[0008]

In the flywheel according to the present invention, the oil component that moves radially inward on the clutch disc side due to the action of centrifugal force during operation fly from the plurality of first through holes formed in the flywheel body. It is discharged to the input side rotating body side of the wheel body. In addition, the oil component moving in the first through hole non-forming portion (predetermined interval portion) includes a plurality of second through holes arranged corresponding to the interval portion radially outward of the first through hole forming portion. Is similarly discharged to the input side rotating body of the flywheel body.

As described above, since the first and second through holes are equivalent to the through holes formed around the entire circumference of the flywheel main body in terms of oil discharge, the flywheel main body on the clutch disc side. The oil that moves can be effectively discharged to the input side rotating body side of the flywheel body. As a result, it is possible to suppress the oil content from reaching the clutch disc side and prevent the clutch from slipping.

[0010]

FIG. 1 shows a flywheel as an embodiment of the present invention. Here, a split flywheel provided with a liquid viscosity damper mechanism is taken as an example. This flywheel includes an input-side first flywheel 1, an output-side second flywheel 6 rotatably supported by the input-side first flywheel 1 via bearings 5, a first flywheel 1 and a first flywheel 1. Liquid viscous damper mechanism arranged between the two flywheels 6 (hereinafter simply referred to as damper mechanism)
And 60. The first flywheel 1 is fixed to the crankshaft of the engine, and the second flywheel 6 is equipped with a clutch 7.

The first flywheel 1 is a generally disk-shaped member, and is formed continuously with a boss portion 1a which is arranged at the center and fixed to a crankshaft (not shown) of the engine by a bolt 18. Side plate portion 1b that is extended radially outward
And a flywheel portion 1c continuously formed on the outer peripheral side of the side plate portion 1b. The boss portion 1a is the second
It projects to the flywheel 6 side, and the second flywheel 6 is rotatably supported on the outer periphery of this projection via a bearing 5. The bearing 5 is fixed by a plate 19 mounted on the end surface of the boss portion 1a with a screw 22. The stopper plates 2 are arranged facing the side plate portion 1b at a predetermined interval. The stopper plate 2 is detachably attached to the side plate portion 1b with a bolt 3. The damper mechanism 60 is inserted between the side plate portion 1b and the stopper plate 2. The damper mechanism 60 is unitized by pins and the like, and can be easily attached to and detached from the side plate portion 1b by removing the bolt 3.

The second flywheel 6 is a generally disc-shaped member, and has a boss portion 6a arranged at the center, a pressure contact portion 6b formed continuously from the boss portion 6a and extending in the radial direction, and an outer periphery of the pressure contact portion 6b. And a clutch mounting portion 6c formed continuously on the side. The boss portion 6 a projects toward the first flywheel 1 side, and the inner circumference of the projecting portion is supported by the bearing 5. Further, as shown in FIG. 2, corrugated external teeth 14 to which the damper mechanism 60 is connected are formed on the outer peripheral portion. The clutch-side end surface of the press contact portion 6b is a friction surface 6d with which the friction member of the clutch disc 11 forming the clutch 7 presses. The friction surface 6d projects from the end surface on the same side of the boss portion 6a, and as shown in an enlarged view in FIG. 3, a concave receiving portion 5 is formed on the inner peripheral surface of the projection portion.
2 is formed in a circumferential shape. The receiving portion 52 is for receiving oil that moves outwardly in the radial direction on the clutch disc 11 side end surface of the second flywheel 6 by the action of centrifugal force during operation.

Further, the second flywheel 6 is provided with a through hole 53 for discharging the oil component received by the receiving portion 52 to the first flywheel 1 side. As shown in FIG. 4, a plurality of through holes 53 are formed on the circumference at predetermined intervals, and each through hole 53 is an elongated hole extending in the circumferential direction. Further, each through hole 53 widens toward the first flywheel 1 side. As a result, the oil component that has entered the through holes 53 can be easily discharged from the through holes 53 to the first flywheel 1 side.

Further, in the second flywheel 6, a plurality of penetrating holes which penetrate the second flywheel 6 and extend obliquely outward in the radial direction are provided inward in the radial direction of the portion where the through holes 53 are not formed. The hole 54 is formed. Each through hole 54 is for discharging the oil component moving on the clutch disc 11 side of the second flywheel to the first flywheel 1 side as shown in FIG. 4.

A clutch cover assembly 8 constituting the clutch 7 is mounted on the end surface of the clutch mounting portion 6c. The clutch cover assembly 8 includes a cover 8a, a pressure plate 9, a diaphragm spring 10 and the like. A clutch disc 11 is arranged in the clutch cover 8. Next, the damper mechanism 60 will be described.

The damper mechanism 60 has an output driven plate 12 composed of a pair of plate members. As shown in FIG. 2, corrugated internal teeth 13 that mesh with corrugated external teeth 14 formed on the outer periphery of the boss portion 6 a of the second flywheel 6 are formed on the inner peripheral portion of the driven plate 12. This allows the driven plate 12 and the second flywheel 6 to rotate integrally.

As shown in FIG. 2, the driven plate 12 is formed with a plurality of window holes 15 at predetermined intervals in the rotational direction. Further, recesses 16 and 17 are formed in the side plate portion 1b and the stopper plate 2 corresponding to the window hole 15, respectively. The window hole 15 and the recesses 16 and 1
Inside the coil 7, a torsion torque transmitting coil spring 20 is arranged so as to be compressible in the rotational direction. The coil spring 20 has spring seats 21 arranged at both ends thereof.
It is in contact with both end faces in the circumferential direction of the window hole 15 via (the same applies to the recesses 16 and 17). However, in the damper disk free state, as shown in FIG. 2, only the inner peripheral side end of the coil spring 20 is in contact with both circumferential end surfaces of the window hole 15. That is, the coil spring 20 is accommodated in the window hole 15 in a biased state.

On the outer side in the radial direction of the driven plate 12, as shown in the exploded perspective views of FIGS. 1 and 5, the side plate portion 1 is formed.
An annular liquid chamber housing 30 sandwiched by b and the stopper plate 2 is arranged. As shown in FIGS. 2 and 5, the liquid chamber housing 30 has a plurality of weir portions 30c at predetermined intervals in the circumferential direction.
0c projects inward in the circumferential direction. In addition, the weir 30c
A pin insertion hole 32 is formed in this. The liquid chamber housing 30 includes a plurality of housing members 30 extending in the circumferential direction.
And the weir portion 30 of these members 30A.
By overlapping c and connecting them by the pin 33, an annular liquid chamber for containing the liquid is formed. A pair of annular projections 30a is formed at the radially inner end of the liquid chamber housing 30, and the liquid projection is sealed by fitting the annular projections 30a into the annular grooves 31 formed in the driven plate 12. is doing. Further, both axial ends and outer circumferential end portions of the liquid chamber are closed by the wall surface of the liquid chamber housing 30.

In the liquid chamber housing 30, a slider 35 is arranged slidably in the circumferential direction. The slider 35 is formed in a box shape having an opening on the inner side, and an outer peripheral wall radially outward is formed in an arc shape along the outer peripheral wall 30b of the housing 30. A pair of leg portions 37 is formed on the inner side portions of both ends of the slider 35 in the circumferential direction, and the liquid circulation openings 50 are formed between the leg portions 37.

In FIG. 2, the leg portion 37 of the slider 35 is shown.
Is slidably in contact with the outer peripheral edge of the driven plate 12. A protrusion 36 is formed at the radially outer end of the driven plate 12 so as to project radially outward. The slider 35 is arranged so as to accommodate the protrusion 36 inside. Both side walls in the circumferential direction of the slider 35 are stopper portions 35a, and the stopper portions 35a are spaced from the projection 36 by a predetermined distance in the circumferential direction, for example, by angles θ1 and θ2 when the engine is stopped. The projection 36 partitions the liquid chamber in the slider 35 into a first sub-compartment 40 in the front in the rotational direction and a second sub-compartment 41 in the rear in the rotational direction, and both the sub-compartments 40, 41 between the inner surface with the slider 35. To form a sub-choke S1.

A main choke S2 is formed between the radially inner peripheral edge of the weir portion 30c and the outer peripheral edge of the driven plate 12 so as to connect the first and second large chambers 45 and 46 adjacent to each other. ing. The distance between the main choke S2 is the sub choke S1.
Is smaller than the interval. That is, the flow cross-sectional area of the sub-choke S1 is larger than the flow cross-sectional area of the main choke S2.

The driven plate 12 has a liquid supply passage 47 formed in its wall. Liquid supply passage 47
Is the slider 3 at the radially outer edge of the protrusion 36.
It is open to the 5 side. The liquid supply passage 47 extends radially inward from the opening, branches into two, and opens in the window hole 15, respectively. Next, the operation of the above embodiment will be described.

When a twisting torque is generated during operation, the first flywheel 1 is twisted with respect to the driven plate 12 in the rotation direction forward direction or the rotation direction backward direction. At this time,
In the range of small torsion angle, the coil spring 20 is biased and compressed, so that the flywheel exhibits small torsional rigidity. When the torsion angle becomes large, the coil spring 20 is totally compressed, so that the flywheel exhibits a large torsional rigidity.

The generation of hysteresis due to the movement of the liquid when the twisting torque is generated will be described in detail. As shown in FIG. 2, the protrusion 36 is the stopper portion 3 of the slider 35.
It is assumed that the first flywheel 1 is twisted with respect to the driven plate 12 in the rotation direction R side in a state where the first flywheel is not in contact with the 5a. In this case, the housing 30
Similarly, the slider 35 also moves to the rotation direction R side. As a result, the second sub-compartment 41 is compressed and becomes smaller, and at the same time, the first sub-compartment 40 is expanded and enlarged.
As a result, the liquid mainly flows from the second small compartment 41 to the first small compartment 40 through the sub-choke S1. Here, the flow passage resistance is small because the cross-sectional area of the flow passage of the liquid flowing from the second small division chamber 41 to the first small division chamber 40 is large. Therefore, a small hysteresis torque is generated here.

When the twist angle increases and the stopper portion 35a on the rear side in the rotation direction comes into contact with the protrusion 36, the sub-choke S1 is closed by closing the slider opening 50, and the slider 35 protrudes. It is fixed by 36. Therefore, the first flywheel 1 and the housing 30 move forward in the rotational direction R with respect to the driven plate 12 and the slider 35.
As a result, the liquid in the second large chamber 46 flows through the main choke S2 to the first large chamber 45 rearward in the rotational direction, and also passes through the gap between the outer peripheral side surface of the slider 35 and the housing 30 and the like. It also flows to the first large branch chamber 45. Here, since the main choke S2 has a small cross-sectional area, a high fluid resistance is generated and a large hysteresis torque is generated.

During the power transmission, the liquid in the housing 35 is normally moved to the outer peripheral side of the damper mechanism 60 by the action of the centrifugal force. However, the liquid is resisted against the centrifugal force by the operation of the damper mechanism 60 and is moved in the radial direction. To the annular projection 30a.
There is a case where it moves through the seal portion of the coil spring 20 and into the gap 25 (FIG. 3) between the bosses 1a and 6a below the coil spring 20 (see arrow A in the figure). In such a case, if the sealing performance of the bearing 5 deteriorates due to long-term operation, the liquid in the gap 25 may leak through the bearing 5 to the space 51 on the side of the bearing 5. This liquid is discharged to the first flywheel 1 side through the through hole 54 by the action of centrifugal force.

On the other hand, the liquid in the portion where the through hole 54 is not formed is not recovered by the through hole 54 and moves radially outward on the clutch disk 11 side of the second flywheel 6 by the action of centrifugal force (see FIG. 3 arrow B). Then, the liquid is temporarily stored in the receiving portion 52 and then discharged through the through hole 53 to the first flywheel 1 side. In this embodiment, the second flywheel 6 is used for discharging the liquid.
Since the state is equivalent to the case where the through holes are formed all around, the liquid leaking from the liquid chamber through the bearing 5 is effectively discharged to the first flywheel side. As a result, the liquid from the bearing 5 is suppressed from reaching the clutch disc 11 side, and as a result, the slip of the clutch disc 11 due to the adhesion of oil is prevented.

[Other Embodiments] In the above embodiment, the split type flywheel provided with the liquid viscous damper was described as an example, but the present invention is not limited to this and is similarly applicable to an integrated flywheel. .

[0029]

Since the flywheel according to the present invention is provided with the oil discharge mechanism including the first and second through holes as described above, the clutch can be prevented from slipping.

[Brief description of drawings]

FIG. 1 is a cross-sectional view of an embodiment of the present invention, taken along line I- of FIG.
I sectional view.

FIG. 2 is a partial side view of the embodiment.

FIG. 3 is an enlarged partial view of FIG.

FIG. 4 is a partial side view of FIG.

FIG. 5 is an exploded perspective partial view of a liquid chamber housing.

[Explanation of symbols]

 1 First Flywheel 6 Second Flywheel 11 Clutch Disc 53, 54 Through Hole

Continuation of the front page (51) Int.Cl. ⁶ Identification code Office reference number FI technical display location 8312-3J F16F 15/30 E

Claims (1)

[Scope of utility model registration request] 1. A flywheel main body which is connected to an input side rotating body and has a friction surface on which a friction member of an output side clutch disc can press-contact, and a predetermined circumference on the circumference radially inward of the flywheel main body. A plurality of first through holes formed at intervals to discharge the oil component moving on the clutch disc side by the action of centrifugal force to the input side rotating body side of the flywheel main body, and the friction in the flywheel main body. A plurality of second through holes for discharging the oil, which are formed radially inward of the surface and radially outward of the first through hole forming portion so as to correspond to the spacing portions. A flywheel equipped with an oil discharge mechanism.