KR101043554B1 - Dual mass flywheel, in particular for a motor vehicle - Google Patents

Abstract

The present invention relates in particular to a dual mass flywheel for automobiles. The invention comprises a first flywheel 10 fixed to an input shaft, a second flywheel 18 and a vibration damper for rotatably connecting these two flywheels, the vibration damper being a radial spring 26. It includes. The first flywheel 10 also includes a flexible circular plate 12 that supports the circular mass 14 and is connected to the spring ring 58, which spring ring 14 damps axial bending vibrations. Are centered and guided.

Description

Damping Dual Flywheels for Automobiles {DUAL MASS FLYWHEEL, IN PARTICULAR FOR A MOTOR VEHICLE}

The invention relates in particular to damping double flywheels for motor vehicles.

As is known, the motor vehicle is equipped with a damping double flywheel between the output shaft and the clutch of the internal combustion engine, which are coaxial with each other and are first and second inertial flywheels, which are centered and guided by the bearings when rotating over each other. It includes a flywheel. A spring-loaded torsion damper is mounted between the two flywheels, and the two flywheels are coupled to rotate together with angular displacement relative to each other.

In traditional technology, the spring of the torsion damper is circumferentially arranged and is usually mounted in an annular chamber filled with grease. In operation, these springs are pressurized by centrifugal force to contact the radially outer wall of the annular chamber and it is possible to compress and relax while ensuring torque transfer between the two flywheels by the grease filling the annular chamber.

It has already been proposed to replace circumferentially arranged springs with substantial radial springs, which are much more sensitive to centrifugal forces, and are better able to absorb irregularities in rotational torque and vibration generated by the vehicle's internal combustion engine. To help.

In addition, in the conventional type of damping dual flywheel, the first flywheel is a rigid component, which is usually manufactured by casting, and in one piece together with a cylindrical hub supporting a bearing for centering and guiding the second flywheel. Is formed.

The damping double flywheel described in French Laid-Open Patent Publication No. 2,662,759 has a circumferential spring mounted in the annular chamber, the first flywheel serving as a flexible component, supporting the annular chamber of the torsion damper and absorbing axial vibration or vibration Type that is configured to

However, in this known device, no means are provided for quickly damping axial vibrations or tremors absorbed by the flexible first flywheel.

The main object of the present invention is to provide a simple, effective and inexpensive solution to this problem.

Summary of the Invention

The present invention teaches, in particular, for a damping dual flywheel for automobiles, which has a radial spring and also has a torsion damper of the type which allows axial vibration or vibration to be absorbed and damped.

To this end, the present invention is coaxial with each other, and the first inertia flywheel and the second inertia flywheel, which are centered and guided by the bearings when they rotate in overlap with each other, so that the two flywheels rotate together but allow angular displacement with respect to each other. In a damping dual flywheel for automobiles comprising a torsion damper with a radial spring mounted between the two flywheels, the first flywheel comprising a flexible annular plate, the radially outer portion of the annular plate being annular. The inertial mass, the radially inner portion thereof being configured to be fixed on a drive shaft, wherein means for damping during axial bending in connection with the flexible annular plate are supported by the annular inertial mass We propose a damping double flywheel for cars.

Thus, in the damping double flywheel according to the invention, rotational vibration and torque irregularities are best absorbed by the torsion damper with radial spring, and axial vibration and vibration are also effectively absorbed and damped. In addition, the means for damping the axial vibration and tremor are supported by an annular inertial mass which is itself supported by the flexible annular plate constituting the first flywheel, so that the capacity to damp axial vibration and tremor Constant and does not depend on the axial bending of the first flywheel.

In a first embodiment of the invention, the inertial mass comprises an axial stack of annular rings fixed to each other and to the flexible annular plate, wherein the axial stack of the annular ring is subjected to friction between these rings. Thereby constitutes means for damping during axial bending.

The axial bending of the flexible annular plate supporting the stack of annular rings is in fact converted to a weak displacement between these rings, and the friction caused by this weak displacement causes the axial bending of the first flywheel to Absorb at least part of it.

In another embodiment, the means for damping during axial bending comprises an elastic ring coaxial with a flexible annular plate, wherein an inner circumference (or outer circumference) of the elastic ring is applied on the flexible annular plate. The outer periphery (or inner periphery) of the elastic ring is applied and centered on the radial flange or shoulder of the inertial mass.

Thus, all axial bending of the first flywheel is converted to the weak axial deformation of the elastic ring described above, and correspondingly energy absorption occurs.

The elastic ring may be disposed axially between the two inertial flywheels.

In another variant, the resilient ring may contact on a face not facing the second flywheel in the flexible annular plate.

The radial flange of the annular inertial mass supported by the flexible annular plate is fixed on the side of the cover plate fixed on the same side as the second flywheel in the inertial mass, or on the side not facing the second flywheel in the inertial mass and It may consist of a metal plate supporting the crown.

In the damping dual flywheel according to the invention, the bearing for centering and guiding the second flywheel is supported by a cylindrical hub connected with the flexible annular plate of the first flywheel.

In these embodiments, the flexible annular plate of the first flywheel can be centered on the cylindrical surface of the hub fixed by screws on the end of the drive shaft with the flexible annular plate.

In another embodiment, the flexible annular plate of the first flywheel is welded on the hub and can be fixed on the end of the drive shaft by a screw, the screws being spaced at regular intervals around the hub.

In another embodiment, the flexible annular metal plate of the first flywheel is fixed on the end of the drive shaft by a screw, the hub has a radial flange for application and fastening on the flexible annular metal plate, The radial flange of the hub is fixed on the metal plate by screws or rivets, the screw fastens the annular flexible metal plate on the drive shaft, the drive shaft having a predetermined gap and a hole present in the radial flange of the hub. Or through the cutout.

In a variant embodiment, an annular plate is interposed between the flexible annular plate and the radial flange of the hub, the radial flange is fixed on the annular plate by screws or rivets, and the annular plate is screwed by a screw. It is fixed itself to a flexible annular plate on the end of the drive shaft.

Preferably, in this case, the hub has an axial flange at its end located on the same side as the first flywheel, the axial flange supporting and centering the flexible annular plate and the annular plate, It serves to center the hub on the end of the drive shaft.

The radial spring of the torsion damper is mounted on the radial rod in the cylindrical housing, the radially inner end of the radial rod is fitted in a cavity present in the annular member, and the annular member is rotationally driven by the second flywheel. The annular member cooperates with friction means for damping vibrations and rotational vibrations between the flywheels.

The means generates proper friction during the angular displacement between the two inertial flywheels, damping the rotational vibration and torque irregularities generated by the internal combustion engine.

1 is a schematic front view of a damping dual flywheel according to the present invention, in which a second flywheel is shown on the left side and a second flywheel is not shown on the right side;

FIG. 2 is a schematic cross sectional view taken along the line II-II of FIG. 1;

3 shows half of the axial cross section of a modified embodiment of the invention,

4 to 6 are schematic axial cross-sectional views of another embodiment of the present invention;

7-9 are schematic perspective views of the components of FIG. 6 on different scales.

Further features, details, advantages, and the like of the present invention will be more clearly understood from the following description and the accompanying drawings.

The damping dual flywheel shown schematically in FIGS. 1 and 2 is basically a flexible annular metal plate 12 and an annular fixed by screws 16 on the radially outer circumference of the flexible annular metal plate 12. A first inertial flywheel 10 composed of an inertial mass 14; A second inertial flywheel (18) consisting of two annular components (20, 22) coaxially coupled to each other via a torque limiter (24); A torsion damper having a radial spring 26 mounted in the cylindrical housing 28 between these inertial flywheels 10, 18.

The starter crown 30 is fixed on the outer circumference of the annular inertial mass 14. The radially inner periphery of the flexible annular plate 12 has a cylindrical hub 34 which supports a bearing 36 for centering and guiding the first annular component 20 of the second flywheel 18 in rotation. Is centered on the axial flange 32 of. The axial flange 32 of the hub 34 also serves to center the hub on the end of a drive shaft (not shown), such as the crankshaft of the internal combustion engine of the motor vehicle.

The hub 34 also has a radial flange 38 on the side opposite to the second flywheel 18, through which the rivet 40 is fixed to the flexible annular plate 12. do. The assembly consisting of the flexible annular plate 12 and the hub 34 is fixed on the end of the drive shaft by screws 42 spaced at regular intervals about the common axis of rotation 44 of the flywheels, and the pitch circle The diameter of the screw on is larger than the outer diameter of the bearing 36.

Holes 46 formed in the first annular component 20 of the second flywheel 18 allow access to the head of the screws 42 and, if necessary, to the passages of these screws.

The cylindrical housing 28 which receives the radial torsion damper spring 26 is pivoted at its radially outer end on the pivot pin 48 supported by the inertial mass 14 of the first flywheel 10. The springs 26 are mounted on axial rods 50 inside the housing 28, the radially outer ends of each of these rods supporting a thrust ring for the springs 26, and the radially inner ends are pins. Pivoted by 52 on first annular component 20 of second flywheel 18.

Between the two inertial flywheels, friction means 54, 56 are mounted to absorb their relative angular displacements.

In the damping double flywheel according to the invention, an axially acting elastic ring 58, such as a Belleville ring, is connected with the flexible annular plate 12, so that the flexible annular plate 12 during axial bending. Damping vibrations and vibrations of the elastic ring 58, which is positioned between two inertial flywheels, whose radially inner circumference is attached on the flexible annular plate 12, while its radially outer circumference is It is attached and centered on the shoulder 60 of the inertial mass 14 of the first flywheel 10.

The shoulder 60 is not a continuous circle in this embodiment, but is formed only in the middle of each space separating the two continuous cylindrical housings 28 between the cylindrical housings 28 of the torsion damper.

The annular inertial mass 14 itself is in the form of a “V” shaped cavity or groove, which receives the housing 28 of the torsion damper spring and is fastened and pivoted on the first flywheel 10 by means of a pivot pin 48. Allows the housing 28 to be tilted about the pivot pin 48. On the same side as the second flywheel 10 in the inertial mass 14 of the first flywheel, a radial cover plate 62 is fixed by rivets, which also has a "V" shaped cut. A portion or slot, which allows the housing 28 of the torsion damper spring fastened to the first flywheel 10 by the pin 48 to pivot about the pin 48.

In this damping double flywheel according to the invention, all rotational vibrations or torque irregularities generated by the internal combustion engine are transmitted to the first flywheel 10 via the drive shaft and are converted into angular displacements between the two flywheels and thus friction Damped by means 54, 56.

Similarly, any vibrations or vibrations during axial bending transmitted to the first flywheel 10 via the drive shaft are absorbed by the flexible annular plate 12 and the flexible annular plate 12 and the inertial mass. Damped by an elastic ring 58 mounted between the 14. Due to this particular configuration, whatever the vibration and deformation during axial bending of the annular plate 12 is, the force applied on the flexible annular plate 12 by the elastic ring 58 is substantially constant.

In the modified embodiment shown schematically in FIG. 3, the structure of the damping dual flywheel is substantially the same as that shown in FIGS. 1 and 2, with the difference that the elastic ring 58 is connected to the flexible annular plate 12. A cover plate 62 centered on the radial flange 66 of the inertial mass 14 of the first flywheel and fixed on the same side as the second flywheel in the annular mass 14. Is axially contacted on the inner radial flange 68.

Except for this, the components of this embodiment are the same as or similar to the corresponding components shown in FIGS. 1 and 2, and are denoted by the same reference numerals.

In the modified embodiment of FIG. 4, the basic difference from the above-described variant is that the elastic ring 58 connected with the flexible annular plate 12 of the first flywheel is not located between the inertial flywheels 10, 18. And is attached on the side of the flexible annular plate 12 facing the drive shaft 70, supporting the starter crown 30 and on the inertial mass 14 and the annular plate 12 by means of rivets 74. The radial outer circumference thereof is held by the annular metal plate 72 which is fixed.

In addition, the radially inner circumference of the flexible annular plate 12 is welded on the end of the axial flange 32 of the hub 34, and the assembly composed of the flexible annular plate 12 and the hub 34 is driven. It is centered on the distal shoulder of the shaft 70. Furthermore, only the flexible annular plate 12 is fixed on the end of the drive shaft 70 by the screw 42, and the head of the screw 42 into the recess present at the corresponding end of the hub 34. Extend freely.

The operation of this embodiment is the same as that of the above-described embodiment.

5 shows that the elastic ring 58 is attached on the same side as the drive shaft 70 of the engine in the flexible annular plate 12 but not between the first flywheel 10 and the second flywheel 18. 4 is repeated, the basic difference from the variant of FIG. 4 being that the inertial masses 14 of the first flywheel are axially superimposed on one another, on each other and on the plate 72 described above. Consisting of rings 78 fastened with rivets 74, the cover plate 62 being riveted on the same side as the second flywheel 18 in the final ring 78, and further annular metal plate It is fixed to the plate 72 by the 80.

In this embodiment, all of the axial bending of the annular plate 12 is converted into a small frictional bond between the rings 78, so that the rings 78 are of the energy from the axial bending of the annular plate 12. Absorb at least part of it.

The cylindrical hub 34 also has a radial flange 38 at an end located on the same side as the drive shaft 70, by means of the radial flange 38 in the radial direction of the annular plate 12. Riveted on the periphery. The annular plate 12 is itself fixed on the end of the drive shaft 70 by screws 42, the head of the screws 42 into the recesses present in the peripheral flange 38 of the hub 34. Extend freely.

The radially inner end of the rod 50 supporting the spring 26 of the torsion damper fits into a recess present in the annular member 82 made of, for example, plastic material or other suitable material, and the annular member 82 ) Is rotationally driven by the first annular component 20 of the second flywheel 18 and to the friction means 54 and the cylindrical hub 34 supported by the flexible annular plate 12 of the first flywheel 18. Flanges 84 and 86, respectively, which cooperate with the friction means 56 supported by it, are provided to damp rotational torque and torque irregularities generated by the internal combustion engine and transmitted through the drive shaft 70.

6 to 9 repeat substantially the same structure as described with reference to FIGS. 1 and 2, the basic difference being that the annular plate 90 is cylindrical with the flexible annular plate 12 of the first flywheel. Interposed between the radial flanges 38 of the hub 34 and the flexible annular plate 12 on the axial flange 32 of the hub 34 centering the assembly on the drive shaft 70. Is centered together. The radial flange 38 of the hub 34 is fixed on the annular plate 90 by rivets 92, which together with the flexible annular plate 12, are attached to the screw 42. By itself being fixed on the end of the drive shaft 70, the head of the screw 42 extends freely into the cutout or recess present in the radial flange 38 of the hub 34. An axially oriented dowel 94 can cause the assembly consisting of the flexible annular plate 12, the annular plate 90 and the cylindrical hub 34 to be positioned in a rotational orientation on the end of the drive shaft 70. Make sure The flexible annular plate is also provided by two radially opposing screws, which pass through the hole 96 of the annular plate 90 and also through the corresponding hole 98 of the radial flange 38 of the cylindrical hub 34. It is advantageous to have the annular plate 90 fixed on 12.

The radial outer periphery of the annular plate 90 is connected by a first flywheel 10 and by means of a second flywheel 18 via a pivot pin 52 which engages the radial rod 50 of the torsion damper. With respect to the annular member 104 supporting the friction means 106 connected with the driven means, it is fixed by a rivet 100 fitted into the hole 102 of the annular plate 90.

Claims (16)

Coupling the flywheels with the first inertial flywheel 10 and the second inertial flywheel 18, which are coaxial with each other and centered and guided by the bearing 36 when rotating in superimposition with one another, but with an angle to each other. In a damping dual flywheel for an automobile comprising a torsion damper with a radial spring 26 mounted between the two flywheels to enable displacement, The first inertial flywheel 10 includes a flexible annular plate 12, wherein a radially outer portion of the flexible annular plate 12 supports the annular inertial mass 14, and the flexible annular plate ( The radially inner portion of 12 is configured to be fixed on the drive shaft 70, wherein means for damping during axial bending in connection with the flexible annular plate 12 are provided by the annular inertial mass 14. Characterized in that supported Damping double flywheel for cars. The method of claim 1, The annular inertial mass 14 comprises an axial stack of annular rings 78 fixed to each other and to the flexible annular plate 12, wherein the axial stack of the annular rings 78 is between these rings. Characterized in that it constitutes means for damping during axial bending by friction of Damping double flywheel for cars. The method of claim 1, The means for damping during axial bending includes an elastic ring 58 coaxial with the flexible annular plate 12, wherein an inner circumference of the elastic ring 58 is on the flexible annular plate 12. And the outer periphery of the elastic ring 58 is attached and centered on the shoulder 60 of the annular inertial mass 14. Damping double flywheel for cars. The method of claim 3, wherein The shoulder 60 is characterized in that it is not a continuous circle Damping double flywheel for cars. The method of claim 3, wherein The elastic ring 58 is characterized in that it is disposed axially between the two inertial flywheels (10, 18) Damping double flywheel for cars. The method of claim 3, wherein The elastic ring 58 is held axially by the radial flange 68 of the cover plate 62 fixed on the same side of the annular inertial mass 14 as the second inertial flywheel 18. Characterized by Damping double flywheel for cars. The method of claim 3, wherein The elastic ring 58 is characterized in contact with the surface of the flexible annular plate 12 not facing the second inertial flywheel 18. Damping double flywheel for cars. The method of claim 7, wherein The radial flange is fixed on the side opposite to the second inertia flywheel 18 in the annular inertial mass 14 and is formed on a metal plate 72 supporting the starter crown 30. By Damping double flywheel for cars. 9. The method according to any one of claims 1 to 8, The flexible annular plate 12 is centered on an axial flange 32 of the cylindrical hub 34, and the axial flange 32 of the cylindrical hub 34 is the flexible annular plate 12. Is fixed on the end of the drive shaft 70 and supports a bearing 36 for centering and guiding the second inertial flywheel 18. Damping double flywheel for cars. The method of claim 9, The axial flange 32 of the cylindrical hub 34 centers the cylindrical hub 34 on the drive shaft 70 at an end located on the same side as the first inertial flywheel 10. Characterized in that Damping double flywheel for cars. 9. The method according to any one of claims 1 to 8, The flexible annular plate 12 is fixed by welding on a hub 34 that supports a bearing 36 for centering and guiding the second inertial flywheel, and at regular intervals around the hub 34. It is fixed on the end of the drive shaft 70 by screws 42 spaced apart by Damping double flywheel for cars. 9. The method according to any one of claims 1 to 8, The flexible annular plate 12 is fixed on the end of the drive shaft 70 by a screw 42 and a hub 34 supporting a bearing 36 for centering and guiding the second inertial flywheel. ) Has a radial flange 38 for attachment and fastening on the radially inner portion of the flexible annular plate 12. Damping double flywheel for cars. 13. The method of claim 12, The radial flange 38 of the hub 34 is fixed on the flexible annular plate 12 by screws or rivets, and fastening the flexible annular plate 12 on the drive shaft 70. The screw 42 for freely passing through the cutout or recess of the radial flange 38 Damping double flywheel for cars. 13. The method of claim 12, An annular plate 90 is interposed between the flexible annular plate 12 and the radial flange 38 of the hub 34, the radial flange being connected by screws or rivets 92 to the annular plate 90. And the annular plate 90 is itself fixed to the flexible annular plate on the end of the drive shaft 70 by means of a screw 42. Damping double flywheel for cars. The method of claim 14, The hub 34 has an axial flange at its end located on the same side as the first inertial flywheel, the axial flange supporting and supporting the flexible annular plate 12 and the annular plate 90. And center the hub 34 on the end of the drive shaft. Damping double flywheel for cars. The method of claim 9, The radial spring 26 of the torsion damper is mounted on the radial rod 50 in the cylindrical housing 28, the radially inner end of the radial rod 50 being in the annular member 82. And the annular member 82 is rotationally driven by the second inertial flywheel 18, and the annular member 82 is damped with vibrations and rotational vibrations between the inertial flywheels 10, 18. Characterized in that it has flanges 84, 86 cooperating with friction means 54, 56 for Damping double flywheel for cars.

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