WO2011150911A2

WO2011150911A2 - Rotary vibration damper

Info

Publication number: WO2011150911A2
Application number: PCT/DE2011/001085
Authority: WO
Inventors: Hartmut Mende; Kornelia Bartel
Original assignee: Schaeffler Technologies Gmbh & Co. Kg
Priority date: 2010-05-31
Filing date: 2011-05-19
Publication date: 2011-12-08
Also published as: CN102918297B; DE112011101864A5; CN102918297A; WO2011150911A3; DE102011101977A1

Abstract

The invention relates to a rotary vibration damper (1) having two flywheel masses (3, 4) which are mounted one on top of the other about an axis of rotation (2) of said rotary vibration damper and which are rotatable relative to one another to a limited extent about said axis of rotation counter to the action of a spring device. In order to improve the vibration decoupling behaviour of a rotary vibration damper arranged in particular in the drivetrain of a motor vehicle, an annular mass pendulum (11) is provided which is mounted centrally relative to the axis of rotation and which, when the two flywheel masses rotate relative to one another, is driven in rotation over a limited angle of rotation by one of the two flywheel masses.

Description

Drehschwinqunqsdämpfer

The invention relates to a torsional vibration damper, in particular in the drive train of a motor vehicle with two about an axis of rotation of these superimposed and this against the action of a spring device against each other begr rotatable flywheel masses.

Such torsional vibration dampers are well known, for example in the form of dual-mass flywheels and have long been used in series. In this case, the two flywheel masses are mounted on an axis of rotation against each other against the action of a spring device preferably formed from bow springs. If torsional vibrations are recorded in such a D he vibration damper, with appropriate compression of the Federein direction egg ne intermediate storage of torque peaks in the spring means and ei ne delayed and gedäm pfte delivery to the drive train. Among other things, the quality of the vibration isolation depends on the stimulating frequency of, for example, an internal combustion engine in the form of a diesel engine and the torque to be transmitted via the torsional vibration damper. In this case, the damping behavior wors with increasing torque to be transmitted as a result of necessarily designed with higher stiffness spring means under given space conditions.

There are therefore - as for example known from DE 10 2004 011 380 A 1 - proposed combined with a centrifugal pendulum torsional vibration damper, where z addition to an effective between two disc parts in the circumferential direction Federerein direction distributed over the circumference and with respect to a about the axis of rotation Rotary vibration damper rotating T ägerteil limited pivotable pendulum masses are arranged and form a speed-adaptive vibration absorber. These pendulum masses each pivot about a pendulum axis radially outside de r rotation axis and have a high number of parts with a plurality of bearings on the support member, which are exposed to high centrifugal forces. Due to the necessary distance of the pendulum masses from each other to avoid mutual contact, the maximum available mass moment of inertia of the pendulum masses is relatively small in the available space. The object of the invention is therefore to improve a torsional vibration damper with respect to a cost-effective and robust integration of a Tilgerelements with a reduction in the number of parts and a simple storage.

The object is achieved by a torsional vibration damper, in particular in the drive train of a motor vehicle with two about an axis of rotation of these superimposed and this against the action of a spring device against each other limited rotatable masses, with an axis of rotation centric mounted, annular mass pendulum is provided, which at a rotation of the both shot masses are rotationally driven by one of the two flywheel masses over a limited angle of rotation.

By only a single mass part in the form of the mass pendulum, which is arranged so that it can be displaced limitedly about the axis of rotation, the number of parts can be reduced and the bearing can be formed in a simple manner. The drive of the mass pendulum with changing direction of rotation, rotational speed or rotational acceleration takes place by means of a Drehtt- measure against a Schw ung mass, which is only slightly loaded and can be stored in a simple manner. By a single annular mass pendulum, the mass moment of inertia of the tilgenden masses against m ehreren, distributed over the order circumferential pendulum masses, for example, be increased by 3 to 5 times. The drive of the mass pendulum with changing angle of rotation causes especially when the flywheels are excited by rotational shocks ei nen vibration-damping effect.

The rotary driving as rotary coupling of the mass pendulum against one of the two masses can thereby by means of at least one, preferably more evenly distributed over the circumference, rotatably mounted between the mass pendulum and the flywheel mounted in the other flywheel, each forming a power transmission such as teeth with the flywheel and the mass pendulum Ritzel's are formed. Other power transmissions may be, for example, other torque transmitting coupling elements such as frictional Abrollgeometrien, crank joints and the like.

The or designed as plug-in shafts with corresponding external gears for the mass pendulum and the driving S chwungrad sprocket are stored in the other flywheel e efacher manner, for example by means of plastic bushings. In this case, the secondary flywheel can drive the mass pendulum, wherein the pinion are taken as plug-in waves in the primary flywheel rotatable. Alternatively, the primary Flywheel drive the mass pendulum. In di esem case, the stub shafts are rotatably housed in the secondary flywheel or a component connected to this, for example, the energy store of the spring device acting on Flanschtei l rotatable. In the case of an embodiment without flywheel masses or in a separate arrangement of these, the mass pendulum can be controlled by an input - or output-side component such as disk part as driven and corresponding teckwellen or pinion be rotatably arranged in the other input-or output-side component.

It can be provided between the mass pendulum and this driving S chwungmasse a translation, so that when changing the Drehbes acceleration of the flywheel mass pendulum is driven depending on the direction of rotation with a translation into Fast or Slow. Here, between the pinions and the

Flywheel on the one hand and the mass pendulum on the other hand formed gears are translated differently, the number of teeth and / or the effective diameter can be configured differently. A rotation of the M essependels can be provided in the same direction of rotation as the driving flywheel, the pinion with a corresponding external teeth each with respect to the axis of rotation of the torsional vibration damper radially outside or radially inside a corresponding Zahnprof il the mass pendulum and the flywheel drehsc luiquely intervene. If an opposite rotation of the mass pendulum is achieved, for example, engage the pinion by means of an external toothing radially outwardly into a toothing part and by means of the other external toothing in the other toothing part of the mass pendulum or the flywheel. Experiments have ben ben shown here that depending on the E properties of the internal combustion engine, for example, depending on the number of cylinders and thus introduced into the drive train torsional vibrations, for example 2nd order, the effect of the torsional vibration damper with respect to these torsional vibrations dependent on the translation and the Direction of movement of the mass pendulum against the driving S tung mung mass is. For example, in four-cylinder diesel engines with a maximum torque in excess of 300Nm, speed-to-speed ratios of 1.0 to 1.8 preferably 1 to 2 to 1.6 and slow-to-0.8 to -0.1 are preferred from -0.6 to -0.2 proved to be particularly advantageous. It is understood that with corresponding properties of the internal combustion engine, for example gasoline engines or diesel engines with a different number of cylinders, for example between three and eight cylinders different preferred translations can prove advantageous. The mass pendulum can be formed in one piece. For example, the mass pendulum can be formed from sheet metal, wherein radially outward to increase the mass moment of inertia several sheet metal layers can be folded onto each other. Radially inside, the mass pendulum can be mounted on a bearing flange. The bearing flange of a flywheel can form the storage for the other flywheel on the same or a different diameter. The teeth to form the teeth with the pinions can be issued directly from the sheet or formed from corresponding flared sheet metal parts. The storage can be a sliding or roller bearing. It has also proven to be particularly advantageous if the mass pendulum is formed from a carrier part forming a toothing and a bearing seat and a riveted, such as riveted, for example formed as a casting or Scrimiedeteil.

In this case, the mass pendulum can be arranged on a side opposite the secondary flywheel mass of a primary flywheel. In such an embodiment, the mass pendulum is arranged quasi outside of the torsional vibration damper and facing the wall of Brennk raftmaschine. The primary flywheel can be indented at least in the radially outer region, so that the mass pendulum is arranged radially within an axial projection, which can accommodate, for example, the starter ring gear.

To further improve the isolation effect may additionally one or both

Flywheels are assigned to a centrifugal pendulum effectively. For this purpose, in addition to the mass pendulum, a plurality of pendulum masses distributed over the circumference and limitedly pivotable relative to a carrier part are provided. For example, the spring device acting on the output side as the secondary side acting flange part as a support member and radially absorb the P endelmassen within the spring means.

The invention will be explained in more detail with reference to the embodiments shown in Figures 1 to 12. Showing:

FIG. 1 shows a partially sectioned view, directed from the transmission side, of a torsional vibration damper according to the invention;

FIG. 2 shows a view, directed from the motor side, of the torsional vibration damper of FIG. 1,

3 shows the torsional vibration damper of Figure 1 in section along the section line YY, 4 shows the torsional vibration damper of FIG. 1 in section along the section line XX, FIG.

FIG. 5 is an exploded view of the torsional vibration damper of FIG. 1;

6 shows a partial section through a relative to the torsional vibration damper

FIG. 1 shows a modified vibration damper with rotating mass pendulum, which is translated in opposite directions to the driving mass.

7 shows a partial section through a relative to the torsional vibration damper

FIG. 6 shows a modified version of the damping pendulum with the mass pendulum rotating in the same direction as the driving mass,

8 shows a partial section through a relative to the torsional vibration damper

FIG. 6 shows a modified version of the vibration damper with mass pendulum rotating in opposite directions to the driving vibration mass without transmission;

Figure 9 shows a partial section through a Drehsc vibration damper of the

primary flywheel driven mass pendulum,

FIG. 10 is a partial view of the torsional vibration damper of FIG. 9;

1 1 shows a partial section of a torsional vibration damper from the primary

Flywheel driven mass pendulum and compared to the torsional vibration damper of Figure 9 modified storage of Ri tzel and

FIG. 12 shows a partial view of the torsional vibration damper of FIG.

Figures 1 and 2 show the rotating about the rotation axis 2, to egg ner crankshaft of an internal combustion engine such as diesel engine with four cylinders recorded torsional vibration damper 1 in the form of a dual mass flywheel from the Getriebesei te ago (Figure 1) and from the motor side (Figure 2) , The two flywheel masses 3, 4, of which the flywheel 3 is attached at the input side as a primary flywheel by means of mounting holes 5 on the crankshaft and the flywheel 4 serves as a counter-pressure plate to be fastened on this Reibun gskupplung s ind one another by means of the bearing 6 the action of the spring means 7, which is formed here of two Bogenfe- 8, limited against each other displaced. Hierz u are not visible on the primary flywheel 3 indentations and provided on the secundary flywheel 4 at the radially connected thereto Flanschteii extended arms 10.

In addition to the drehschw ingungsdäm pfenden effect of the opposite to the spring device 7 limited rotatable Sc hwungmassen 3, 4 of the torsional vibration damper with the schwingungstitenden mass pendulum 11 is provided, which is rotationally driven at a rotation of the two n flywheel masses 3, 4. For this purpose, distributed over the circumference in the primary flywheel 3 rotatably pinion 12 are received, the both sides of the recording in the primary flywheel 3 external teeth 13, 14, which with teeth 15, 16 in the flange part 9 and the mass pendulum 11, the teeth 17, 18th form in accordance with a P lanetengetriebe, in which the primary flywheel 3 as between the secondary flywheel 4 and the mass pendulum 11 switched web can be considered, the secondary flywheel 4 so the mass pendulum 11 rotatably drives. The toothing 17 is arranged radially on the inside of the flange part 9 and the toothing 18 radially on the outside of the mass pendulum 11, so that the drive of the mass pendulum takes place in opposite directions of rotation. Furthermore, by the larger diameter diameter of the external teeth 14 of the teeth 18 on the mass pendulum 11 with respect to the external teeth 13 of the teeth 17 on the flange 9 and thus the secondary flywheel 4 a translation of the mass pendulum 11 relative to the secondary flywheel 4 is achieved quickly.

Figures 3 and 4 show the torsional vibration dam fer 1 of Figure 1 along the

Cut lines X-X and Y-Y, respectively. The primary flywheel 3 is fixed on the bearing part 19, the secondary flywheel 4 rotatably received by means of the radially provided within the mounting holes 5 storage 6 as rolling bearings. The mass donation! 11 is radially outside the mounting holes 5 by means of the bearing 20 - hi er a sliding bearing - rotatably received on the bearing part 19. Radial inside is provided on the bearing part 19, the pilot bearing 27 for receiving a transmission input shaft, not shown.

The mass pendulum 11 is made in two parts from the support member 21 made of sheet metal and the ground ring 22. These are connected to each other by means of the rivet 23. The support member is provided with corresponding recesses 24 to form the axially shaped toothing parts 16 which are separated from one another by respective webs 25 in the circumferential direction. Radially inside is on the support member 21 of the axial projection 26 angef formed to form the storage 20.

The pinion 12 as stub shafts with their external teeth 13, 14 si nd rotatably mounted by means of plastic bushings 28 in corresponding openings in the primary flywheel 3. When the two masses of inertia 3, 4 are rotated relative to one another, the bores genspredern 8 input side of the recesses 29 of the primary flywheel and the output side of the arms 10 of the connected to the secondary flywheel 4 by means of the rivets 30 flange member 9 compressed. The rotation takes place, for example, upon transmission of a torque entered by the engine in the torsional vibration dam 1. In this case, rotational shocks, Drehsc vibrations and derglei surfaces are saved by kurzeitige increases the angle of rotation in the spring means 7 and released time-delayed again, so that ei ne vibration damping occurs. With a change in the angle of rotation, the pinion 12 is driven by means of the toothing 17, this driving with the set ratio of the toothing 17 the mass moment of inertia formed with a predetermined M inertia 11 in the opposite direction, so that the recorded by rotational shocks and torsional vibrations kinetic energy is eradicated, so that overall an improved vibration isolation is achieved. In this case, translations between the secondary flywheel 4 and the mass pendulum 11 of 1, 0 to 1, 8, in particular between 1, 6 and 1, 2 have proven to be particularly effective for a vibration damping.

Figure 5 shows the torsional vibration damper 1 in the form of an exploded view with the pilot bearing 27 receiving bearing part 19 on which the support member 21 is rotatably received with the attached by means of the rivets 23 mass ring 22 and the sliding bearing 31. With the bearing part 19, the primary flywheel 3 and the reinforcing plate 32 is further secured and centered connected, with a firm connection via the mounting holes 5 after screwing on the crankshaft. The primary flywheel 3 continues to receive radially outside the starter ring gear 33 and is completed by the pulley parts 34, 35 and the wear shells 36 and the sealing ring 37 to form the radially inner open annular chamber in which the bow springs 8 are inserted and the flange part 9 is inserted , The pinions 12 are in the openings 38 of the primary

Inertia 3 stored. The flange 9 is riveted by means of the rivets 30 with the secondary flywheel 4. The centering pins 39 are for centered receiving a clutch pressure plate of a friction clutch introduced into the secondary flywheel 4.

Figure 6 shows a partial section through a torsional vibration damper 1 of Figures 1 to 5 similar torsional vibration damper 101, in which on the flange 109 in addition and circumferentially between the teeth 115 forming recesses 140 limited relative to the flange portion 109 displaceable pendulum masses 141 on both sides of the flange 109th to form a centrifugal pendulum such as in the

DE 10 2004 011 380 A 1 are disclosed. FIG. 7 shows a partial section through a torsional vibration damper 1 of FIGS. 1 to 6 similar to torsional vibration damper 201. In contrast to these, an equidirectional rotary drive of the mass pendulum 211 is provided, i ndem the external teeth 213, 214 of the pinion 212 each with the teeth 215, 216 of the flange 209 and the mass pendulum 211 radially outside the V erzahnungen 217, 218 form. In the same way, in other embodiments, the teeth can each be formed radially inward.

FIG. 8 shows a rotary oscillation damper 301 corresponding to the rotary oscillation dampers 1, 101, 201 with an opposite rotational drive of the axial pendulum 31 1 by the secondary flywheel 304 by means of the flange part 309. By the external teeth 313, 314 formed with the same diameter gl eicher number of teeth formed pinion 312 is between the flange 309 and the mass pendulum 31 1 no translation ung or the ratio 1, 0 set.

FIGS. 9 and 10 show the torsional vibration damper 401 in partial section and in FIG

Partial view in which the mass pendulum 411 is driven by the primary flywheel 403. For this purpose, bolts 441 are received on the flange part 409, on which the pinions 412 are secured by means of the retaining rings 442 and are received rotatably. The primary flywheel 403 has recesses 440 m with Verzahnungstei len 415, the teeth 417 bil with the external teeth 413 d he sprocket, while the outer teeth 414 416 forms the teeth 418 with the mass pendulum 41 1 with the Verzahnungstei. The Ausführungsbeis shown piel shows an opposing rotational drive b of the mass pendulum 41 1 by the primary flywheel 403 corresponding to the torsional vibration dampers 1, 101, 301 of Figures 1 to 5, 6 and 8.

In contrast to the torsional vibration damper 401 of Figures 9 and 10, Figures 11 and 12 show the D rehschwingungsdämpfer 501 in partial section and in partial view also with the primary flywheel 503 rotationally driven mass pendulum 511. In contrast to the torsional vibration damper 401 is the translation ung the mass pendulum 511 in the opposite direction, for example between -0.8 and -0.1, preferably between -0.5 and -0.3. For this purpose, the external toothing 513 of the delimitation 51 7 to the primary flywheel 503 a size ren diameter or a larger number of teeth than the external teeth 514 of the teeth 518 z mass pendulum to 511 on. It is understood that by forming the teeth on both sides radially outside or radially inside a rotary drive can be provided in the same direction of rotation. To record the crack! 512 on the flange portion 509 is expressed from this, the dome 543, at the axially overlapping the pinion 512 are received by means of the bolt 541.

LIST OF REFERENCES

Torsional vibration damper

axis of rotation

Inertia

fastening opening

storage

spring means

bow spring

flange

poor

mass pendulum

pinion

external teeth

toothed piece

gearing

bearing part

storage

support part

ground ring

rivet

recess

web

approach

Püotlager

Plastic bushing

indentation

rivet

bearings

Reinforcing Schei be

Starter gear

disk part disk part

Usefulness

seal

opening

Centering

torsional vibration dampers

flange

toothed piece

recess

pendulum masses

Torsional vibration damper

flange

mass pendulum

Ritzet

external teeth

toothed piece

gearing

Three vibration dampers

Inertia

flange

Mass donation l

pinion

external teeth

Torsional vibration damper

Inertia

flange

mass pendulum

pinion

external teeth

Toothing l

Toothing l 417 toothing

418 toothing

440 recess

441 bolts

442 Circlip

501 torsional vibration damper

503 flywheel

509 flange part

511 mass pendulum

512 pinions

513 external toothing

514 external toothing

517 toothing

518 toothing

541 bolts

543 Dom

X-X cutting line

Y-Y intersection line

Claims

claims

1. torsional vibration damper (1, 101, 201, 301, 401, 501) in particular in the drive train of a motor vehicle with two about an axis of rotation (2) of these superimposed and this against the action of a spring means (7) against each other limited rotatable masses (3, 4, 304, 403, 503), characterized gek ennzeichnet that a to the axis of rotation (2) centrally mounted, annular mass pendulum (11,

211, 311, 411, 511) is provided which, upon rotation of the two pivoting masses, is rotationally driven relative to one another by one of the two flywheel masses (3, 4, 304, 403, 503) over a limited angle of rotation.

2. torsional vibration damper (1, 101, 201, 301, 401, 501) according to claim 1, characterized in that between the mass pendulum (11, 211, 311, 411, 5 11) and the flywheel (4, 304, 403, 503) at least one in the other flywheel (3) rotatably mounted, with the flywheel (4, 304, 403, 503) and the mass pendulum (11, 211, 311, 411, 511) a power transmission ausbi Idendes form the pinion (12 .

212, 312, 412, 512) is effective.

3. Torsional vibration damper (1, 201, 401, 501) according to claim 2, characterized g ekennzeichnet that the power transmission such as gears (17, 18, 217, 218, 417, 418, 517, 518) unterschiedl I translations of a flywheel (4 , 304, 403, 503) and the mass pendulum (11, 211, 311, 411, 511).

4. torsional vibration damper (1, 101, 201, 301, 401, 501) according to any one of claims 2 or 3, characterized gek ennzeichnet that the mass pendulum (11, 211, 311, 411, 511) from a toothing (18, 218 , 318, 418, 518) and a support (21) forming a bearing (20) and a grounding ring (22) attached thereto.

5. torsional vibration damper (1, 101, 201, 301) according to one of claims 1 to 4, characterized in that the mass pendulum (11, 211, 311) by a secondary flywheel (4, 304) is driven.

6. torsional vibration damper (401, 501) according to one of claims 1 to 4, characterized in that the pinion (412, 512) of a secondary flywheel is rotatably associated and the mass pendulum (411, 511) of a primary flywheel (403, 503 ) is driven.

7. torsional vibration damper (1, 101, 201, 301, 401, 501) according to one of claims 1 to 6, characterized in that the mass pendulum (11, 211, 311, 41 1, 511) on one of the secondary flywheel (4, 304) opposite side of a primary flywheel (3, 403, 503) is t. Torsional vibration damper (201) according to one of claims 1 to 7, characterized in that the mass pendulum (211) in the direction of rotation of the torsional vibration damper (201) is driven.

Torsional vibration damper (1, 101,301,401, 501) according to one of claims 1 to 7, characterized in that the mass pendulum (11, 311, 411, 511) against the rotational direction of the torsional vibration damper (1, 101, 301, 401, 501) is driven.

Torsional vibration damper (101, 201, 301) according to one of claims 1 to 7, characterized in that in addition to the mass pendulum (211, 311) a plurality of distributed over the circumference relative to a support member limited pivotable pendulum masses (141) are provided.