JP2003004101A - Torque transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve the damping potential of a torque transmission device. SOLUTION: The torque transmission device comprises a first flywheel mass body 3 adapted to be joined to the output shaft of an internal combustion engine and a second flywheel mass body 4 adapted to be connected/disconnected to/ from a transmission via a clutch. Both flywheel mass bodies are supported in a mutually turnable manner against the operation of a damper 9 arranged therebetween. The damper 9 has an energy accumulator 10 to be effective in the peripheral direction. The energy accumulator is stored in a circuit chamber 11. The circuit chamber is formed by utilizing the section of at least one flywheel mass body. Two damper masses 19a, 19b distributed all over the periphery are stored in the circuit chamber. The damper masses are centrifugally supported by at least one component 15 of one flywheel mass body.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a torque transmission device, which can be connected / disconnected to / from a transmission via a first flywheel mass body which can be coupled to an output shaft of an internal combustion engine. A second bounce mass is provided, both bounce masses being rotatably supported relative to one another against the action of a damping device arranged between them. The device is provided with an energy store which is effective in the circumferential direction, the energy store being at least partly housed in an annular space or an annular chamber, the annular chamber being provided with two proof masses. The present invention relates to a type formed by utilizing a section of a flywheel mass body of at least one of the bodies.

[0002]

The object of the invention is to improve the damping potential of a torque transmission device of this type used as a torsional vibration damper. Furthermore, it is desirable to ensure a space-saving configuration or a compact configuration of the torque transmission device. Furthermore, it is desirable for the torque transmission device formed according to the invention to be particularly simple and inexpensive to manufacture.

[0003]

At least a part of the above-mentioned problems is provided in a torque transmission device of the type described at the beginning, in which the torque transmission device is provided with a torsional vibration attenuator, and the torsional vibration attenuator is Having at least two attenuator masses distributed over the circumference, said attenuator masses being
At least partially contained in the annular chamber, the energy store is also provided in the annular chamber, the attenuator mass being at least one of the bounce masses. Can be solved by being supported by at least one of the components on the basis of centrifugal force.

[0004]

The damper masses are in this case supported on said at least one component in such a way that these damper masses can tend to carry out a circumferentially directed rocking movement. And is advantageous. That is, at least two attenuator masses may be provided in the annular chamber, these attenuator masses being radially spaced from the axis of rotation of the torque transmitting device, The reciprocating motion can be carried out around this axis of rotation.

It can be particularly advantageous if the attenuator mass is arranged radially inward or radially outward of the energy store. However, it is also conceivable for such an attenuator mass to be provided both on the outside and on the inside in the radial direction of the energy store. Furthermore, the attenuator masses are such that they are arranged at an axial height which is at least approximately the same as the axial height of the energy accumulator when viewed in the axial direction of the torque transmission device. It can be advantageous if it is formed and arranged. This can ensure that the attenuator mass does not require additional axial construction space.

[0006] The attenuator masses are particularly preferably provided if they have a natural frequency related to the number of revolutions,
Alternatively, it may be pivotally attached to one component of the torque transmitting device so as to have a vibration absorbing characteristic or a damping characteristic adapted to the rotational speed.

The annular chamber, which at least partially contains the energy store and the attenuator mass, can particularly preferably be at least partially filled with a viscous medium. This viscous medium preferably has at least lubricating properties and may be formed, for example, by grease. With such a configuration of the torque transmission device, it is possible to easily perform the lubrication of the holding portion or the bearing portion required to support the damper mass body based on the centrifugal force.

The suspension or bearing of the attenuator mass is advantageously arranged in at least one movement trajectory, starting from the position where the center of gravity of the attenuator mass is at the maximum distance from the axis of rotation of the damping device. It may be formed so as to be able to reciprocate toward the displacement position along the circumferential direction of the torque transmission device. The attenuator mass is suspended like a pendulum, or is a bifila.
It is advantageous to have a double pivot or suspension of a type similar to r).

With respect to the structure and function of the torque transmission device, one of the bobbin mass bodies mainly forms the annular chamber, and the other bobbin mass body has a flange-like or disc-like shape. A component is fixed, the component is fixed to the other bounce mass in a radially inner region and extends radially outward into the annular chamber, and It can be particularly advantageous for the part to carry a load range for the energy store and serve for radial support of the inertial mass.

The inertial mass body has a sector shape or a cheek shape.
It may simply be formed by one component. The two components are rigidly connected to each other and house a flange-shaped component between them, which component at the same time
It can also serve to load an energy store provided between the two flywheel masses. Advantageously, the flange-shaped component may be provided with a plurality of notches.
These cutouts form a trajectory for the circumferential displacement of the attenuator mass. The cheek-shaped component forming one attenuator mass may have a plurality of notches or recesses, which are at least partially seen in the axial direction of the torque transmission device. In addition, it overlaps with a notch provided in the flange-shaped component. In this case, bearings are accommodated in these recesses, via which the damper mass is supported by centrifugal force against the flange-shaped component while at the same time being movable. Becomes These bearings may be formed, for example, by bearings that extend parallel to the axis of rotation of the torque transmission device, for example rollers.

The attenuator masses are formed in such a way that these attenuator masses, when viewed in the circumferential direction of the torque transmission device, are clamped against one another at the maximum possible displacement.
Alternatively, it may be dimensioned in the circumferential direction. By displacing the attenuator mass with respect to the theoretical rest position (ie without torsional vibrations) occupied by the attenuator mass under the action of centrifugal force, the attenuator mass tends to It is gradually displaced in the direction of the rotation axis of the torque transmission device. Due to this gradual offset of the attenuator masses towards smaller diameters, the circumferential spacing between the individual attenuator masses can be reduced. In this case, this distance is in some cases eliminated sufficiently, that is to say that at least one damping element or spring element is provided between adjacent attenuator masses or between adjacent attenuator masses. Works. By such means or configuration, metallic collision noise at the maximum displacement of the attenuator mass can be at least reduced. It may be advantageous for the attenuator mass to be loadable via at least one energy store. Such an energy store can be provided at least between two attenuator masses which are adjacent to one another in the circumferential direction. In addition or as an alternative, at least one damping intermediate layer can be provided between two attenuator masses which are circumferentially adjacent to one another. This intermediate layer may, for example, consist of plastic or rubber.

Further advantages of the invention with regard to structure and function type are explained in more detail below with reference to the drawings.

[0013]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described in detail below with reference to the drawings.

The torsion damping device (torsion damper device) 1 shown in FIGS. 1 to 3 is formed by a flywheel or a flywheel 2. The flywheel 2 is divided into two flywheel elements 3,4. Both flywheel elements 3 and 4 have a support device 5
Are concentrically positioned so as to be rotatable relative to each other. The bearing device 5 can, as can be seen in the drawing, be designed as a sliding bearing or also as a rolling bearing. If a slide bearing is used, this slide bearing is particularly preferably corresponding to the slide bearing disclosed in DE-A 19834729 or DE-A 19834728. It may be formed. German Patent Application Publication No. 1983472
On the basis of the specification No. 9, there are likewise known configurations of rolling bearings, which can advantageously also be used in the subject matter described here. The bearing device 5 is particularly preferably designed in such a way that it is arranged concentrically, but radially inward of a plurality of screw fastening holes 6 provided in one flywheel element 3. is there. In such a configuration, it is advantageous if the flywheel element 4 on the transmission side is also provided with a corresponding cutout 7.
These notches 7 at least partially overlap the screw fastening holes 6 formed as notches in the axial direction. Through these cutouts 7, at least the screw to be screwed into the cutout 6 can be manipulated. Also, cutout 7
May be formed such that the corresponding screw head can be guided axially therethrough. One flywheel element 3 is connectable to the output shaft of the internal combustion engine, and the other flywheel element 4 is connected to the transmission input shaft via a friction clutch to be fixed to this flywheel element 4. It can be shut off. For this purpose, the flywheel element 4 is provided with a friction surface 8 which can at least cooperate with the friction facing of the clutch disc.

A damper 9 is provided between the flywheel elements 3 and 4. This damper 9 comprises a plurality of energy accumulators 10 which are effective in the circumferential direction.
These energy accumulators 10 are formed by coil springs which are effective in the circumferential direction in the illustrated embodiment. These coil springs may be of elongated shape and may already be pre-curved before assembly, depending on their arrangement in the torsion damping device 1. These energy stores 10 are housed in an annular chamber or an annular chamber 11, which can be at least partially filled with a viscous medium, for example grease. The annular chamber 11 is formed mainly by two housing parts 12, 13 which are manufactured as sheet metal parts in the exemplary embodiment shown.
Both housing parts 12, 13 are designated 14 on the outside in the radial direction.
They are welded together at the points indicated by.

When viewed in the circumferential direction, the annular chamber 11 is divided into a plurality of individual accommodating portions at least in the radial range of the energy accumulator 10, and the energy accumulator 10 is provided in these accommodating portions. There is. When viewed in the circumferential direction, the individual housings are separated from one another by load ranges which, in the exemplary embodiment shown, are introduced into both housing parts 12, 13 which are embodied as sheet metal parts. It is formed by a stamping part (Ampregung). Both housing parts 1 forming an annular chamber 11
With regard to the possible configurations of 2, 13 and of the energy store 10 housed in the annular chamber 11, DE-A 37 21 711,
German patent application DE 3721712, German patent application DE 4117582 and German patent application DE 4117.
No. 579.

A plurality of load ranges 1 for the energy store 10 provided on the second flywheel element 4.
4 is supported by a disk-shaped component portion 15. This disc-shaped component 15 is connected further radially inward to the second flywheel element 4 via a rivet connection 16. The load range 14 is
It is formed by a radial bracket or arm integrally molded to the outer contour of the disc-shaped component 15. These arms 14 are, in the axial direction, in the axial direction, with the flywheel 2 unstressed by torque, of the thin housing part 1 of the first flywheel element 3.
2 and 13, provided between the load ranges located opposite each other.

At the time of relative rotation between both flywheel elements 3, 4 in the direction of engine braking operation (operation in which the wheels drive the engine) or in the direction of traction operation (operation in which the engine pulls the wheels), The energy stores 10 are compressed between the load ranges associated with these energy stores 10. In the illustrated embodiment, the two coil springs in and out of one another of the energy store 10 are loaded or supported by the arm 14 at one of its ends simultaneously or immediately during traction operation. It By "towing" is meant that the power plant or engine delivers drive torque for the vehicle.

During engine braking, both coil springs forming one energy accumulator 10 are sequentially loaded. This is because only the inner coil spring is initially loaded via the circumferentially projecting support area 17 of the arm 14.

The energy accumulator 10 and the arm 14 are arranged at least substantially rotationally symmetrically when viewed over the entire circumference of the torsion damping device 1. In the embodiment shown, two energy stores 10 are provided, the disc-shaped component 15 having two arms 14 which are located diametrically opposite one another.

The torque rate (Drehm) formed by all the energy accumulators 10 provided on the flywheel 2
The rate may be in the order of 1 to 15 Nm / °, preferably in the order of 2 to 4 Nm / °. The values mentioned in connection with the energy store 10 correspond to static measurements, that is to say with the flywheel 2 not rotating or at very low speeds. .

The energy accumulator 10 formed of a coil spring is supported by a wall partitioning the annular chamber or the annular chamber 11 under the action of centrifugal force. This causes an increasing frictional engagement as the rotational speed increases.

The torsion damping device 1 has a vibration damper 18 in addition to the damper 9 with the energy store 10 working in the circumferential direction. The vibration damper 18 has a large number of inertial mass bodies 19 arranged adjacent to each other in the circumferential direction. These inertial masses 19 are advantageously arranged uniformly in the circumferential direction. The vibration attenuator 18 is designed in the exemplary embodiment to be adapted to the rotational speed, in which case the vibration attenuator 18 has a natural frequency which is proportional to the rotational speed. , It may be designed so as to obtain a damping effect at any rotation speed.

As can be seen from FIGS. 2 and 3, each inertial mass 19 consists of two masses 19a, 19b, both masses 19a, 19b being formed in segments, as can be seen from FIG. And are firmly connected to each other as can be seen in FIG. In this case, both mass bodies 19
In the illustrated embodiment, a and 19b are connected to each other via a rivet connecting portion 20. In the illustrated embodiment, the rivets used to form the rivet joint 20 are
At the same time, it also forms a spacer between the cheek-shaped masses 19a, 19b, in which case the corresponding rivet has a flange-shaped or disk-shaped component 15 which is pivotable with respect to the inertial mass 19. It is formed so as to have properties. To this end, the disk-shaped component 15 has a corresponding through hole or notch (Freischnitt).
These through holes or notches allow corresponding pivotal play between the rivet forming the rivet joint 20 and the disc-shaped component 15.

In the illustrated embodiment, all inertial masses 19 forming the vibration damper 18 are provided radially inward of the energy store 10, and in this case the vibration damper 18 is likewise annular. It is at least partially housed in the chamber 11. This annular chamber 11 is preferably filled with a viscous medium, for example grease, in which case a holding device or bearing device 21 provided for radially supporting the inertial mass 19 is also advantageous. It becomes at least wetted by the viscous medium which has lubricating properties. That is, it must be at least ensured that the viscous medium flows into the area of the bearing device 21 by the relative movements that occur between the individual components when the torsion damping device 1 is put into operation.

In a variant of the embodiment shown, the inertial mass 19 can also be arranged radially outside the energy store 10. In this case, it can be advantageous if the energy store 10 is arranged with a smaller diameter, for example in the radial extent of the inertial mass 19.

As can be seen in FIG. 1, for each inertial mass 19, two bearing or holding devices 21 are provided. In the illustrated embodiment, each bearing device 21 is formed by an opening or notch 22 provided in the disc-shaped component 15 and a rolling element 23 housed in this opening or notch 22. The rolling element 23 projects laterally with respect to the disk-shaped component portion 15,
It supports segment-shaped mass bodies 19a and 19b.
The rolling element 23 is formed by a roller 23 in the illustrated embodiment. The longitudinal axis of the roller 23 extends parallel to the rotation axis 24 of the torsion damping device 1. The rollers 23 extend into recesses or notches 25 provided in the mass bodies 19a, 19b.

As can be seen in particular in FIG. 1, the housings or notches 22, 25 are rolling paths 26, 2 for the rolling elements 23.
Forming 7. These rolling paths 26, 27 and the rolling element 23 start from the intermediate position shown in FIG. 1, that is, the position where the maximum distance between the center of gravity of the inertial mass body 19 and the rotation axis 24 occurs, and A mass body 19 is formed and arranged relative to the disc-shaped component 15 so as to be capable of reciprocating to a displacement position along a motion trajectory defined by both rolling paths 26, 27. ing. During such an oscillating movement of the inertial mass 19 in the centrifugal force region, the center of gravity of the inertial mass 19 approaches the rotation axis 24 at the displacement position. As can be seen from FIG. 1, the rolling path 26 and the rolling path 27 are curved in opposite directions.

That is, when the rotational vibration superposed on the rotational movement of the torsion damping device 1 is generated, the inertial mass body 19 is moved to the position shown in FIG.
From the intermediate position shown in FIG. 4, relative to the disk-shaped component 15, in which case the individual inertial masses 19 are, as can be seen from FIG.
It tends to be displaced from the axis of rotation 24 towards a position with a smaller spacing.

In the embodiment shown, the inertial mass 19 is formed in such a way that it has supporting areas 28, 29, as seen in the circumferential direction, as can be seen from a comparison between FIGS. 1 and 4. Has been done. Through these support areas 28, 29 the relative displacement movement of the inertial mass 19 relative to the position shown in FIG. 1 can be restricted. That is, in such a configuration, the swinging motion of each inertial mass body 19 is not limited via the rolling paths 26 and 27, but indirectly or directly between the adjacent support ranges 28 and 29. It is done by support. The support areas 28 and 29 have the following advantages. That is, these support areas 28, 29 make it possible to avoid, or at least reduce to an acceptable degree, metallic collision noises that may occur due to the oscillating inertial mass 19. . That is, the support ranges 28, 29 allow damping, for example, by viscous medium contained in the annular chamber 11, in which case the support range 28, 29, which may be formed in a planar manner, Pushed between 29. Also,
The adjacent support areas 28, 29 or the side edges of the inertial mass 19 may also be designed to give rise to an amplified hydraulic displacement of the viscous medium. This can be achieved, for example, by engaging profiled features in the region of the side edges 28, 29 in and out of one another. FIG. 4 further illustrates another means or another possibility for damping the oscillating movement of the proof mass 19. These means or possibilities can be used in combination or in a single form. In a first measure, at least one energy store 3 is provided between the end zones of two inertial masses 19 adjacent to each other.
0 is placed. The energy store 30 may be designed so that it also causes friction damping. In the illustrated embodiment, the energy store 30 is designed as a coil spring. However, rubber springs can also be used to advantage.

In the area on the upper left side of FIG.
A second means for damping the rocking movement of the is shown symbolically or in a simplified manner. In this measure, damping layers or damping elements 31, 32 are provided in at least one of the two end areas of the inertial mass 19 which are adjacent to one another. The damping layers or damping elements 31, 32 may be formed, for example, by a rubber coating. Damping layer 31 and / or damping layer 3
2 may be fixed by vulcanization or gluing to the corresponding components forming the inertial mass 19. It is also possible to use at least one form-fitting connection, ie a mating engagement, or also a combination of different fixing types.

The components forming the rolling paths 26, 27, ie the disc-shaped component 15 and the segmented masses 19a, 19b in the illustrated embodiment, provide at least an extremely high hardness or wear resistance. It is particularly advantageous if it is manufactured from a material that can. That is, it is advantageous if these components are manufactured from hardenable and / or case hardenable steel. In this case, the quenching of the corresponding material can also be carried out partially in the corresponding component, i.e. only at the endangered location.

As can be seen from the drawings, the construction and arrangement of the vibration damper according to the invention enables a compact or space-saving construction of the torsion damping device 1. This is because the axial construction space, which is usually necessary for the energy store 10 in most cases, is also used for housing the vibration damper 18. Furthermore, by arranging the vibration damper 18 in the annular chamber or the annular chamber 11, it is ensured that the lubrication of the bearing or the bearing device 21 for the inertial mass 19 can be carried out easily. It

The claims of the claims submitted in the present application are descriptions only, and do not give up on the application for another claim. Applicant reserves the right to apply for a patent for another combination of features merely as disclosed in the description and / or drawings.

References used in the dependent claims refer to alternative constructions of the subject matter of the independent claim according to the features of each dependent claim, to obtain independent subject protection for the combination of the features of the dependent claim cited. It does not mean giving up.

Since the subject matter of the dependent claims may make independent and independent inventions with respect to the known prior art as of the priority claim date, the applicant considers the subject matter of these dependent claims to be the subject matter of the independent claims. Reserve what to do. Further, the subject matter of these dependent claims may also include an independent invention having a separate and independent constitution from the subject matter of the preceding dependent claims.

The invention is not limited to the examples described in the specification. Rather, numerous variations and modifications are possible within the framework of the invention, especially the individual features or members or method steps described in the specification in general and in the examples and in the claims and shown in the drawings. Variations, members and combinations and / or materials which, due to the combination or modification of features, can be inferred by a person skilled in the art in relation to the problem-solving and which result in new features or new method steps or method step sequences by the combined characteristics Also conceivable are manufacturing, testing and working methods.

[Brief description of drawings]

FIG. 1 is a cutaway schematic view of a torque transmission device according to the present invention.

FIG. 2 is a sectional view taken along line II-II of FIG.

3 is a cross-sectional view taken along the line III-III in FIG.

FIG. 4 is a schematic diagram showing the torque transmission device shown in FIG. 1 in a state where the mass bodies of the inertia mass bodies forming the vibration damper are displaced in the circumferential direction.

[Explanation of symbols]

1 torsion damping device, 2 flywheel, 3, 4
Flywheel element, 5 bearing device, 6 screw fastening hole, 7 notch, 8 friction surface, 9 damper,
10 energy accumulator, 11 annular chamber, 12,
13 housing part, 14 load range, 15 disk-shaped component part, 16 rivet connection part, 17
Support range, 18 vibration damper, 19 inertial mass body, 19a, 19b mass body, 20 rivet coupling part, 21 bearing device, 22 notch, 23 rolling element, 24 rotational axis, 25 notch, 26, 27
Rolling path, 28,29 Support range, 30 Energy accumulator, 31,32 Damping element

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Wolfgang Like             Germany Bühl Sonharde               8 (72) Inventor Johann Yeckel             Federal Republic of Germany Baden-Baden             Sponheimer Strasse 10 (72) Inventor Laurent Seebacher             Federal Republic of Germany Neuried-Iche             Nheim Magdalenenstrasse             twenty five (72) Inventor Hartmut Mende             Federal Republic of Germany Buhl Merkelbe             Axel 45

Claims (16)

[Claims] 1. A torque transmission device, wherein a first flywheel mass body connectable to an output shaft of an internal combustion engine and a second flywheel mass body connectable to and disengageable from a transmission via a clutch. Are provided, and the two flywheel masses are rotatably supported relative to each other against the action of a damping device arranged between the two flywheel masses, said damping device in the circumferential direction. An effective energy store, the energy store being at least partially housed in an annular chamber, the annular chamber being at least one of the bounce masses. Of the type formed by utilizing at least two attenuator masses distributed over the entire circumference, the attenuator masses being , Of both the masses A torque transmission device characterized in that it is supported by at least one component of one of the flywheel masses by centrifugal force. 2. The torque transmission device according to claim 1, wherein the attenuator mass is arranged radially inward or radially outward from the energy accumulator. 3. The attenuator mass is arranged at an axial height which is at least approximately the same as the axial height of the energy accumulator when viewed in the axial direction of the torque transmission device. The described torque transmission device. 4. The torque transmission device according to claim 1, wherein the damper mass has a natural frequency related to the rotational speed of the torque transmission device. 5. The attenuator mass has a center of gravity of the attenuator mass as a starting point at a position having a maximum distance from a rotation axis of the damping device, and moves toward the displacement position along at least one motion trajectory. The torque transmission device according to any one of claims 1 to 4, which is capable of reciprocating movement when viewed in the circumferential direction of the torque transmission device. 6. The torque transmission device according to claim 1, wherein the annular chamber is at least partially filled with a viscous medium. 7. The pendulum-guided inertial mass or abutment part of the attenuator mass is lubricated by a viscous medium contained in the annular chamber. The described torque transmission device. 8. The torque transmission device according to claim 1, wherein the attenuator mass is suspended like a pendulum. 9. The torque transmitting device of claim 8, wherein the damper mass is pivotally mounted in a bifilar-like fashion. 10. One of the baffle masses mainly forms the annular chamber, and a flange-shaped component is fixed to the other bounce mass, and the flange-shaped component is fixed to the baffle mass. A component is fixed to the other bounce mass in a radially inner region and extends radially outward into the annular chamber, and the flange-like component further comprises the energy storage. Holding a load range for the vessel, which serves to radially support an inertial mass that acts as a pendulum.
The torque transmission device according to any one of items 1 to 7. 11. An inertial mass body having two cheek-shaped components, both components containing a flange-shaped component between them and rigidly connected to each other. The torque transmission device according to any one of claims 1 to 10, which is present. 12. The flange-shaped component is provided with a notch, the notch defining a movement trajectory for circumferentially displacing the attenuator mass. The torque transmission device according to any one of items 1 to 7. 13. A notch is provided in the cheek-shaped component forming the attenuator mass, the notch being at least partially seen in the axial direction of the torque transmission device. 13. The torque transmission device according to claim 11, wherein the torque transmission device overlaps with the cutouts provided in the shaped component, and the bearing is accommodated in the cutouts. 14. Torque transmission device according to claim 1, wherein the attenuator mass is loaded via at least one energy store. 15. Torque transmission device according to claim 1, wherein at least one energy accumulator is arranged between two attenuator masses which are adjacent to one another in the circumferential direction. 16. The torque transmission device according to claim 1, wherein at least one damping intermediate layer is provided between two damper masses that are adjacent to each other in the circumferential direction.