DE102020117763A1 - torsional vibration damper - Google Patents

Abstract

Torsional vibration damper (1) for damping rotational irregularities of a drive shaft (2) that can be driven by an internal combustion engine, with a damping device (3) which, in the torque flow from the drive shaft (2) to an output shaft (4), has a primary side (5) designed to absorb a torque and a primary side (5) designed to absorb a torque Transmission of the torque to the output shaft (4) arranged secondary side (6), and an absorber system (7); the primary side (5) interacting with the absorber system (7) only via a friction connection (9) acting in relation to a circumferential direction (8); wherein the absorber system (7) forms a first connection (13) which is prestressed at least in relation to an axial direction (11, 12) with a connection element (10) connected to the secondary side (6), the first connection (13) having two opposite axial direction (11, 12) inclined surfaces (14, 15) is formed.

Description

The present invention relates to a torsional vibration damper for damping rotational irregularities of a drive shaft that can be driven by an internal combustion engine, such as a crankshaft, with a damping device that is in the torque flow from the drive shaft to an output shaft, such as. B. a transmission input shaft, a set up for receiving torque primary side and provided for passing the torque to the output shaft secondary side, and an absorber system.

A torsional vibration damper of this type is arranged in particular in a drive train of a motor vehicle between an internal combustion engine and a transmission. The torsional vibration damper can transmit a torque from the input shaft to the output shaft, in particular in a switchable manner. The primary side of the damping device is connected in particular to a clutch disk, which is arranged in a clampable manner between a pressure plate and a counterplate. If the pressure plate is shifted towards the counter plate, the clutch disc is clamped between them and a torque can be introduced into the torsional vibration damper.

A damper system is z. B. provided a centrifugal pendulum and in particular for a reduction of motor-excited torsional vibrations. The absorber system comprises at least one flange (as a flywheel) and a plurality of pendulum masses that are movably arranged on the flange. When the centrifugal pendulum is in operation, the pendulum masses can be used to generate a restoring moment that counteracts a rotational non-uniformity.

A centrifugal pendulum, e.g. B. according to DE 10 2006 028 552 A1 , e.g. B. at least two pendulum masses, which are guided by means of (pendulum) rollers on a carrier element or two carrier elements, hereinafter referred to as (FKP) flange, along a track or guides. The pendulum masses can oscillate along their tracks in the field of centrifugal acceleration if they are excited by the torque fluctuations of an internal combustion engine.

Due to these vibrations, energy is withdrawn from the exciter vibration at suitable times and fed back in again, so that the exciter vibration calms down, i.e. the centrifugal pendulum pendulum acts as an absorber. Since both the natural frequency of the centrifugal pendulum oscillation and the excitation frequency are proportional to the speed, the damping effect of a centrifugal pendulum can be achieved over the entire frequency range.

A damping device is a torsional flexibility introduced in a targeted manner in a drive train excited with periodic disturbances. The aim here is to shift the disruptive vibration resonances that occur in various operating situations to a speed range that is as below the operating speeds as possible. In particular, therefore, the primary side is due to the vibrations relative to the secondary side and z. B. twisted against a spring force. Vibration resonances that remain in the operating speed range are dampened by an external or integrated friction device whose friction torque has to lie within defined limits.

It is known to connect an absorber system, ie its flange, to a hub flange or a driver disk of a clutch disk or to a secondary side of a damping device using rivet bolts.

From the DE 10 2018 109 072 A1 is known to arrange the absorber system in a rotationally fixed manner directly on the hub of a clutch disc.

From the U.S. 2014/182993 A1 It is known to arrange the absorber system in a rotationally fixed manner directly on the hub of a clutch disk, with the connection between the flange of the absorber system and the hub being prestressed by a plate spring.

From the US 4,597,485 A1 is known to use a plate spring to form a bayonet connection.

Proceeding from this, the present invention is based on the object of at least partially overcoming the problems known from the prior art and in particular of specifying a torsional vibration damper in which the damping device and absorber system can be manufactured or assembled independently of one another as pre-assembly groups, then connected to one another and as a common one created in this way Assembly can be arranged on a hub. In particular, the absorber system should also be able to be connected to the damping device to form the torsional vibration damper subsequently (ie after the damping device has been arranged on the hub). In particular, a power transmission between the primary side and the absorber system, in particular in the axial and/or the radial direction, should be at least limited or even avoided. In particular, a play-free connection between absorber system and damping device should be realized.

This object is achieved with a torsional vibration damper according to the features of independent claim 1. Further advantageous refinements of the invention are specified in the dependent claims. The features listed individually in the dependent claims can be combined with one another in a technologically meaningful manner and can define further refinements of the invention. In addition, the features specified in the claims are specified and explained in more detail in the description, with further preferred configurations of the invention being presented.

A torsional vibration damper is proposed for damping rotational irregularities in a drive shaft that can be driven by an internal combustion engine. The torsional vibration damper includes a damping device which, in the torque flow from the input shaft to an output shaft, has a primary side configured to absorb a torque and a secondary side configured to transmit the torque to the output shaft, and an absorber system. The primary side interacts with the absorber system only (that is, exclusively) via a frictional connection acting in relation to a circumferential direction. With a connecting element connected to the secondary side, the absorber system forms a first connection that is prestressed at least in one axial direction, the absorber system having a first surface and the connecting element having a second surface, the first surface and thus the absorber system as a result of the prestress along a first axial direction Is pushed towards the second surface and towards the damping device.

In particular, the torsional vibration damper has a common axis of rotation for the damping device and absorber system components.

The components absorber system (e.g. centrifugal pendulum) and damping device have already been described at the outset. Reference is made to these statements.

In particular, the absorber system has at least one flange, which extends outwards in the radial direction, starting from the first surface. In particular, the flange includes receptacles for pendulum masses and rollers for guiding the pendulum masses.

In particular, the primary side is designed as a driver disk. The primary side is rotatably arranged in particular with respect to a secondary side designed as a hub flange, the secondary side z. B. is rotatably arranged on a hub via a toothing.

The connecting element is in particular firmly connected to the secondary side, e.g. B. rivets or screws.

The absorber system is connected to the damping device in particular via a first connection that acts (only) by friction in the circumferential direction. The surfaces forming this first connection are designed to be inclined (corresponding to one another) with respect to the axial direction, so that in particular a surface contact can be formed between them.

At least one of the surfaces, in particular both surfaces, runs circumferentially along the circumferential direction.

(Further) displacement of the faces along the axial direction is restrained due to the inclination of the faces.

Specifically, each surface forms a tapered surface that extends along the circumferential direction and is inclined along the axial direction from the axial direction. In particular, the surfaces that are in contact with one another thus have a continuously increasing diameter along the first axial direction.

In particular, the absorber system is connected to the connecting element via a bayonet connection. A bayonet connection allows the absorber system to be installed easily. A non- (self-) detachable connection can be realized via the bayonet connection.

In particular, the bayonet connection is formed by a first cup spring and the connecting element.

In particular, the first disk spring is supported on the connecting element with a first edge region pointing inwards in a radial direction opposite a second axial direction opposite the first axial direction and on the absorber system with a second edge region pointing outwards opposite the first axial direction.

The first disc spring is ring-shaped in particular in a known manner and extends in the radial direction from a first edge region to an outer edge region. The first plate spring generates a force acting on the absorber system in the first axial direction. The first plate spring supports itself against the two th axial direction on the connecting element, which itself is stationary on the secondary side (e.g. via rivets or screws).

In particular, the connecting element extends from a first end arranged on the secondary side along the (second) axial direction to a second end, the connecting element having a plurality of first openings at the second end along the circumferential direction. Two extensions of the first disc spring, forming the first edge region, extend along a radial direction through each first opening, each extension forming a positive connection with one side surface of the first opening in relation to the circumferential direction and a first extension adjoining in relation to the second axial direction the connecting element is supported.

In particular, the bayonet connection is formed via the extensions and the first openings.

The connecting element is in particular sleeve-shaped between the first end and the second end. The second surface of the connecting element, which forms the first connection together with the first surface of the absorber system, is arranged at least partially along the axial direction between the first openings and the first end. Preferably, the second surface is located solely between the first openings and the first end along the axial direction. In particular, the second surface is arranged adjacent, in particular immediately adjacent, to the first openings along the axial direction.

In particular, the friction connection is formed by a friction ring extending along the circumferential direction, the friction ring being arranged on the damping device and being freely movable relative to the primary side, at least along the axial direction.

In particular, the friction ring is supported on the absorber system in relation to a second axial direction opposite to the first axial direction and on a spring element in relation to the first axial direction and above that on the secondary side, the friction ring being prestressed in relation to the absorber system and the axial direction via the spring element .

In particular, the absorber system is pressed against the friction ring via the first disk spring.

The spring element is designed in particular as a second plate spring. The spring element is arranged in particular along the axial direction between the friction ring and the secondary side.

In particular, the friction ring has an annular base body and, along the circumferential direction, a plurality of elevations extending in the axial direction, starting from the base body, with at least one elevation extending along the axial direction through a second opening on the primary side to the absorber system, so that the friction ring is arranged in a form-fitting manner on the primary side with respect to the circumferential direction.

As a result of the pivoting of the secondary side relative to the primary side, the frictional connection with the absorber system connected to the secondary side can be formed via the friction ring driven by the primary side.

In particular, the friction ring is arranged on the damping device exclusively via the second openings, aligned with respect to the radial direction. The friction ring is freely movable in the axial direction with respect to the primary side. In particular, the second openings are also so large compared to the elevations that there is play between the second openings and elevations in the radial direction, so that the friction ring is also essentially freely movable in the radial direction in relation to the primary side. In particular, such a position and a movement of the primary side is not influenced by the friction ring or no or only a small force is transmitted in these directions between these components, at least not in relation to the axial direction and possibly also not in relation to the radial direction.

In particular, the primary side is also essentially independent of the movement of the absorber system, since this only interacts with the friction ring and, via the connecting element, only with the secondary side.

1. a) Bereitstellen der Dämpfungseinrichtung als eine Vormontagegruppe, wobei das Verbindungselement an der Sekundärseite der Dämpfungseinrichtung angebunden ist; wobei sich das Verbindungselement von einem an der Sekundärseite angeordneten ersten Ende entlang der axialen Richtung hin zu einem zweiten Ende erstreckt, wobei das Verbindungselement an dem zweiten Ende entlang der Umfangsrichtung eine Mehrzahl von ersten Öffnungen aufweist;
2. b) Bereitstellen des Tilgersystems als eine Vormontagegruppe;
3. c) Aufschieben des Tilgersystems auf das Verbindungselement über das zweite Ende;
4. d) Anordnen einer ersten Tellerfeder an dem Tilgersystem, wobei sich die erste Tellerfeder mit einem, in einer radialen Richtung nach außen weisenden zweiten Randbereich gegenüber der ersten axialen Richtung an dem Tilgersystem abstützt; wobei die erste Tellerfeder entlang der Umfangsrichtung eine Mehrzahl von jeweils zwei, einen in der radialen Richtung nach innen weisenden ersten Randbereich bildende, Fortsätze aufweist;
5. e) elastisches Verformen jeweils eines ersten Fortsatzes, so dass der erste Fortsatz über die erste Öffnung in das Verbindungselement hinein verlagert wird und
6. f) Verdrehen der ersten Tellerfeder gegenüber dem Verbindungselement, so dass jeweils auch der zweite Fortsatz über die Öffnung in das Verbindungselement hinein verlagert wird und Ausbilden der Bajonettverbindung sowie der ersten Verbindung; wobei jeder der zwei Fortsätze mit jeweils einer Seitenfläche der ersten Öffnung eine gegenüber der Umfangsrichtung formschlüssige Verbindung ausbildet und der erste Fortsatz sich gegenüber einer zweiten axialen Richtung an dem zweiten Ende des Verbindungselements abstützt.

A method for assembling the described torsional vibration damper is also proposed, at least comprising the following steps:

1. a) providing the damping device as a sub-assembly, the connecting element being connected to the secondary side of the damping device; wherein the connecting member extends from a first end located on the secondary side along the axial direction to a second end, the connecting member having a plurality of first openings at the second end along the circumferential direction;
2. b) providing the absorber system as a sub-assembly;
3. c) pushing the absorber system onto the connecting element via the second end;
4. d) arranging a first disk spring on the absorber system, the first disk spring being supported on the absorber system with a second edge region pointing outwards in a radial direction relative to the first axial direction; wherein the first plate spring has a plurality of extensions along the circumferential direction, each of two, forming a first edge region pointing inwards in the radial direction;
5. e) elastic deformation of a first extension in each case, so that the first extension is displaced into the connecting element via the first opening and
6. f) twisting of the first disc spring relative to the connecting element, so that the second extension is also shifted into the connecting element via the opening and forming the bayonet connection and the first connection; each of the two extensions forming a form-fitting connection with one side surface of the first opening in relation to the circumferential direction, and the first extension is supported on the second end of the connecting element in relation to a second axial direction.

Steps a) and b) can in particular be carried out in different sequences. Steps c) to f) take place in particular after steps a) and b) and in particular in the specified order.

The invention also relates to a drive train of a motor vehicle, at least comprising an internal combustion engine and a transmission, the torsional vibration damper described being arranged between the internal combustion engine or the drive shaft driven by it and the transmission or the transmission input shaft (referred to here as the output shaft). The torsional vibration damper can transmit a torque from the input shaft to the output shaft, in particular in a switchable manner. The primary side of the damping device is connected in particular to a clutch disk, which is arranged in a clampable manner between a pressure plate and a counterplate. If the pressure plate is shifted towards the counter plate, the clutch disc is clamped between them and a torque from the internal combustion engine can be introduced via the drive shaft and the clutch disc into the torsional vibration damper and passed on via the output shaft to the transmission.

The explanations for the torsional vibration damper can be transferred in particular to the method and the drive train and vice versa.

The use of indefinite articles (“a”, “an”, “an” and “an”), particularly in the claims and the description reflecting them, is to be understood as such and not as a numeral. Correspondingly introduced terms or components are to be understood in such a way that they are present at least once and in particular can also be present several times.

As a precaution, it should be noted that the numerals used here (“first”, “second”, ...) primarily (only) serve to distinguish between several similar objects, sizes or processes, i.e. in particular no dependency and/or sequence of these objects, sizes or make processes mandatory for each other. Should a dependency and/or order be necessary, this is explicitly stated here or it is obvious to the person skilled in the art when studying the specifically described embodiment. If a component can occur several times (“at least one”), the description of one of these components can apply equally to all or part of the majority of these components, but this is not mandatory.

• 1: einen Antriebsstrang;
• 2: einen Torsionsschwingungsdämpfer in einer ersten Seitenansicht im Schnitt;
• 3: den Torsionsschwingungsdämpfer nach 2 in einer zweiten Seitenansicht im Schnitt;
• 4: den Torsionsschwingungsdämpfer nach 2 und 3 in einer Explosionsdarstellung in perspektivischer Ansicht;
• 5: den Torsionsschwingungsdämpfer nach 2 bis 4 in perspektivischer Ansicht;
• 6: einen Ausschnitt des Torsionsschwingungsdämpfers nach 2 bis 4 in perspektivischer Ansicht, gemäß Schritt c) des Verfahrens;
• 7: den Ausschnitt des Torsionsschwingungsdämpfers nach 6 in perspektivischer Ansicht, gemäß der Schritte d) bis f) des Verfahrens;
• 8: den Ausschnitt des Torsionsschwingungsdämpfers nach 6 und 7 in perspektivischer Ansicht, nachfolgend zu Schritt f) des Verfahrens;
• 9: eine bekannte Dämpfungseinrichtung auf einer Nabe in einer perspektivischen Ansicht;
• 10: eine Dämpfungseinrichtung des Torsionsschwingungsdämpfers nach 2 bis 8 in einer perspektivischen Ansicht;
• 11: ein bekanntes Tilgersystem in einer perspektivischen Ansicht;
• 12: ein Tilgersystem des Torsionsschwingungsdämpfers nach 2 bis 8 in einer perspektivischen Ansicht; und
• 13: einen Flansch des Tilgersystems nach 12 in perspektivischer Ansicht.

The invention and the technical environment are explained in more detail below with reference to the attached figures. It should be pointed out that the invention should not be limited by the exemplary embodiments given. In particular, unless explicitly stated otherwise, it is also possible to extract partial aspects of the facts explained in the figures and to combine them with other components and findings from the present description. In particular, it should be pointed out that the figures and in particular the proportions shown are only schematic. Show it:

• 1 : a drive train;
• 2 : a torsional vibration damper in a first side view in section;
• 3 : the torsional vibration damper 2 in a second side view in section;
• 4 : the torsional vibration damper 2 and 3 in an exploded perspective view;
• 5 : the torsional vibration damper 2 until 4 in perspective view;
• 6 : a section of the torsional vibration damper 2 until 4 in a perspective view, according to step c) of the method;
• 7 : the detail of the torsional vibration damper 6 in perspective view, according to steps d) to f) of the method;
• 8th : the detail of the torsional vibration damper 6 and 7 in perspective view, subsequent to step f) of the method;
• 9 : a known damping device on a hub in a perspective view;
• 10 : a damping device of the torsional vibration damper 2 until 8th in a perspective view;
• 11 : a known absorber system in a perspective view;
• 12 : an absorber system of the torsional vibration damper 2 until 8th in a perspective view; and
• 13 : a flange of the absorber system 12 in perspective view.

1 shows a drive train 31 of a motor vehicle, at least comprising an internal combustion engine and a transmission (not shown here), with the described torsional vibration damper 1 being arranged between the internal combustion engine or the drive shaft 2 driven by it and the transmission or the transmission input shaft (referred to here as output shaft 4). is. The torsional vibration damper 1 can switchably transmit a torque from the input shaft 2 to the output shaft 4 . The primary side 5 of the damping device 3 is connected to a clutch disc 34 which, equipped with friction linings 36 , is arranged in a clampable manner between a pressure plate 33 and a counter-plate 32 . If the pressure plate 33 is shifted towards the counter plate 32, the clutch disc 34 is clamped between them and a torque of the internal combustion engine can be introduced into the torsional vibration damper 1 via the drive shaft 2 and the clutch disc 34 and passed on via the output shaft 4 to the transmission.

The secondary side 6 of the torsional vibration damper 1 is arranged in a torque-proof manner on the output shaft 4 via a hub 38 . The absorber system 7 is connected to the secondary side 6 via the first connection 13 via a connecting element 10 . A friction connection 9 is provided between a flange 37 of absorber system 7 and primary side 5 .

2 shows a torsional vibration damper 1 in a first side view in section. 3 shows the torsional vibration damper 1 2 in a second side view in section. 4 shows the torsional vibration damper 1 2 and 3 in an exploded perspective view. 5 shows the torsional vibration damper 1 2 until 4 in perspective view. the 2 until 5 are described together below. To the remarks 1 is referred to.

The torsional vibration damper 1 comprises a damping device 3, which in the torque flow from the input shaft 2 to an output shaft 4 has a primary side 5 set up to absorb a torque and a secondary side 6 set up to transmit the torque to the output shaft 4, and an absorber system 7. The primary side 5 acts together with absorber system 7 only (ie exclusively) via a friction connection 9 acting in relation to a circumferential direction 8 . With a connecting element 10 connected to the secondary side 6, the absorber system 7 forms a first connection 13 that is prestressed at least with respect to an axial direction 11, 12, the absorber system 7 having a first surface 14 and the connecting element 10 having a second surface 15, the first surface 14 and thus the absorber system 7 is pushed onto the second surface 15 and towards the damping device 3 as a result of the prestress along a first axial direction 11 .

The torsional vibration damper 1 has a common axis of rotation 35 for the damping device 3 and absorber system 7 components.

The absorber system 7 is a centrifugal pendulum and is intended to reduce engine-excited torsional vibrations. The absorber system 7 comprises two flanges 37 and a plurality of pendulum masses 39 which are arranged between the flanges and are movably arranged on the flanges 37 . When the centrifugal pendulum is in operation, the pendulum masses 39 can be used to generate a restoring moment that counteracts a rotational non-uniformity.

A damping device 3 is a torsional flexibility introduced in a targeted manner in a drive train 31 excited with periodic disturbances. The aim here is to shift the disruptive vibration resonances that occur in various operating situations to a speed range that is as below the operating speeds as possible. The primary side 5 is thus twisted as a result of the vibrations relative to the secondary side 6 and against a spring force. Vibration resonances remaining in the operating speed range are absorbed via an external friction connection 9 damped, whose friction torque has to lie within defined limits.

The absorber system 7 has at least one flange 37 which, starting from the first surface 14 , extends outwards in the radial direction 18 . In a known manner, the flanges 37 form a receptacle for the pendulum masses 39 and have receptacles for rollers which are provided for guiding the pendulum masses 39 .

The primary side 5 is designed as a drive plate. The primary side 5 is arranged to be rotatable against the spring force of the illustrated spring 40 relative to a secondary side 6 designed as a hub flange, with the secondary side 6 being arranged on a hub 38 in a rotationally fixed manner via teeth.

The connecting element 10 is firmly connected to the secondary side 6, z. B. using rivets or screws (see 4 : there rivets).

The absorber system 8 is connected to the damping device 3 via a first connection 13 which acts only by friction in the circumferential direction 8 . The surfaces 14, 15 forming this first connection 13 are designed to be inclined relative to one another in relation to the axial direction 11, 12, so that a surface contact can be formed between them. Both surfaces 14 , 15 run circumferentially along the circumferential direction 8 . Further displacement of the surfaces 14,15 along the axial direction 11,12 is inhibited due to the inclination of the surfaces 14,15.

Each surface 14, 15 forms a conical surface 14, 15 which extends along the circumferential direction 8 and is inclined along the axial direction 11, 12 with respect to the axial direction 11, 12. The mutually contacting surfaces 14, 15 thus have a continuously increasing diameter along the first axial direction 11.

The absorber system 7 is connected to the connecting element 10 via a bayonet connection 16 . The bayonet connection 16 is formed by a first disk spring 17 and the connecting element 10 .

The first disc spring 17 is supported on the connecting element 10 with a first edge region 19 pointing inwards in a radial direction 18 opposite a second axial direction 12 opposite the first axial direction 11 and with a second edge region 20 pointing outwards opposite the first axial direction 11 on the absorber system 7.

The first plate spring 17 is ring-shaped in a known manner and extends in the radial direction 18 from a first edge area 19 to an outer edge area 20. The first plate spring 17 generates a force acting on the absorber system 7 in the first axial direction 11. In this case, the first plate spring 17 is supported in relation to the second axial direction 12 on the connecting element 10 which is itself arranged in a stationary manner on the secondary side 6 by means of rivets.

The connecting element 10 extends from a first end 22 arranged on the secondary side 6 along the second axial direction 12 to a second end 23, the connecting element 13 having a plurality of first openings 23 at the second end 23 along the circumferential direction 8 . Two extensions 24, 25 of the first plate spring 17, forming the first edge region 19, extend along a radial direction 18 through each first opening 23, each extension 24, 25 having a side face 26 of the first opening 23 with a positive fit relative to the circumferential direction 8 Connection forms and a first extension 24 is supported on the connecting element 10 with respect to the second axial direction 12 . About the extensions 24, 25 and the first openings 23, the bayonet connection 16 is formed.

The connecting element 10 is sleeve-shaped between the first end 21 and the second end 22 . The second surface 15 of the connecting element 10, which forms the first connection 13 together with the first surface 14 of the absorber system 7, is arranged along the axial direction 11, 12 exclusively between the first openings 23 and the first end 21. The second surface 15 is arranged directly adjacent to the first openings 23 along the axial direction 11 , 12 .

The friction connection 9 is formed by a friction ring 27 extending along the circumferential direction 8, the friction ring 27 being arranged on the damping device 3 and being freely movable relative to the primary side 5 at least along the axial direction 11, 12.

The friction ring 27 is supported opposite a second axial direction 12, opposite the first axial direction 11, on the absorber system 7 and opposite the first axial direction 11 on a spring element 28 and above that on the secondary side 6, with the friction ring 27 being opposite via the spring element 28 the absorber system 7 and the axial direction 11, 12 with respect to the primary side 5 is biased.

The absorber system 7 is pressed against the friction ring 27 via the first plate spring 17 .

The spring element 28 is designed as a second plate spring. The spring element 28 is arranged along the axial direction 11, 12 between the friction ring 27 and the secondary side 6.

The friction ring 27 has an annular base body 29 and, along the circumferential direction 8, a plurality of elevations 30 extending from the base body 28 along the axial direction 11, 12, each elevation 30 extending along the axial direction 11, 12 by a respective second opening 41 of the primary side 5 extends towards the absorber system 7 so that the friction ring 27 is arranged in a form-fitting manner on the primary side 5 with respect to the circumferential direction 8 .

As a result of the pivoting of the secondary side 6 in relation to the primary side 5, the friction connection 9 with the absorber system 7 connected to the secondary side 6 can be formed via the friction ring 27 driven by the primary side 5.

The friction ring 27 is arranged on the damping device 3 exclusively via the second openings 41 aligned with respect to the radial direction 18 . The friction ring 27 can be moved freely in the axial direction 11, 12 relative to the primary side 5. The second openings 41 are also so large compared to the elevations 30 that there is play between the second openings 41 and elevations 30 in the radial direction 18 so that the friction ring 27 is also essentially freely movable in relation to the primary side 5 in the radial direction 18 .

6 shows a section of the torsional vibration damper 1 2 until 4 in a perspective view, according to step c) of the method. 7 shows the detail of the torsional vibration damper 1 6 in perspective view, according to steps d) to f) of the method. 8th shows the detail of the torsional vibration damper 1 6 and 7 in a perspective view, subsequent to step f) of the method. the 6 until 8th are described together below. To the remarks 1 until 5 is referred to.

According to step c), absorber system 7 is pushed onto connecting element 10 via second end 22 along first axial direction 11. According to step d), a first plate spring 17 is arranged on absorber system 7, with first plate spring 17 having a , In a radial direction 18 outwardly pointing second edge region 20 compared to the first axial direction 11 on the absorber system 7 or its flange 37 is supported. Along the circumferential direction 8 , the first plate spring 17 has a plurality of two extensions 24 , 25 each forming a first edge region 19 pointing inwards in the radial direction 18 . According to step e), the first extensions 24 are elastically deformed (see arrows), so that the first extensions 24 are displaced into the connecting element 10 via the first openings 23 . According to step f), the first plate spring 17 is rotated (see arrow) relative to the connecting element 10 in the circumferential direction 8, so that the second extension 25 is also displaced into the connecting element 10 via the first opening 23 and the bayonet connection 16 is formed as well as the first connection 13. In 8th It is shown that each of the two extensions 24, 25 forms a positive connection with one side surface 26 of the first opening 23 in relation to the circumferential direction 8 and the first extensions 24 are supported in relation to a second axial direction 12 on the second end 22 of the connecting element 10.

9 shows a known damping device 3 on a hub 38 in a perspective view. 10 shows a damping device 3 of the torsional vibration damper 1 after 2 until 8th in a perspective view. the 9 and 10 are described together below. On the remarks on the 1 until 8th is referred to.

The primary side 5 of the damping device 3, which is connected to the clutch disk 34, is shown here. The primary side 5 can be rotated in the circumferential direction 8 against the spring force of the springs 40 relative to the secondary side 6 , which is connected in a rotationally fixed manner to the hub 38 . In 10 it can be seen that a connecting element 10 is provided and that elevations 30 of the friction ring 27 extend through second openings 41 of the primary side 5 .

11 shows a known absorber system 7 in a perspective view. 12 shows an absorber system 7 of the torsional vibration damper 1 2 until 8th in a perspective view. 13 shows a flange 37 of the absorber system 7 12 in perspective view. the 11 until 13 are described together below. On the remarks on the 1 until 10 is referred to.

The absorber system 7 comprises two flanges 37 and a plurality of pendulum masses 39 arranged between the flanges, which are movably arranged on the flanges 37 . The absorber system 8 according to FIG. 12 can be connected to the damping device 3 via a first connection 13 which acts only by friction in the circumferential direction 8 . The surfaces 14, 15 forming this first connection 13 are designed to be inclined relative to one another in relation to the axial direction 11, 12, so that a surface contact can be formed between them. the The first surface 14 arranged on the absorber system 7 runs all the way around in the circumferential direction 8 .

The first surface 14 forms a conical surface 14 which extends along the circumferential direction 8 and is inclined along the axial direction 11, 12 with respect to the axial direction 11, 12. The first surface 14 thus has a continuously increasing diameter along the first axial direction 11 .

Reference List

1

torsional vibration damper

2

drive shaft

3

damping device

4

output shaft

5

primary side

6

secondary side

7

absorber system

8th

circumferential direction

9

friction connection

10

fastener

11

first axial direction

12

second axial direction

13

first connection

14

first face

15

second surface

16

bayonet connection

17

first disc spring

18

radial direction

19

first border area

20

second edge area

21

first end

22

second end

23

first opening

24

first extension

25

second process

26

side face

27

friction ring

28

spring element

29

body

30

elevation

31

powertrain

32

counter plate

33

pressure plate

34

clutch disc

35

axis of rotation

36

friction lining

37

flange

38

hub

39

pendulum mass

40

feather

41

second opening

QUOTES INCLUDED IN DESCRIPTION

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Patent Literature Cited

• DE 102006028552 A1 [0004]
• DE 102018109072 A1 [0008]
• US2014182993A1 [0009]
• US 4597485 A1 [0010]

Claims (10)

Torsional vibration damper (1) for damping rotational irregularities of a drive shaft (2) that can be driven by an internal combustion engine, with a damping device (3) which, in the torque flow from the drive shaft (2) to an output shaft (4), has a primary side (5) designed to absorb a torque and a primary side (5) designed to absorb a torque Transmission of the torque to the output shaft (4) arranged secondary side (6), and an absorber system (7); the primary side (5) interacting with the absorber system (7) only via a friction connection (9) acting in relation to a circumferential direction (8); wherein the absorber system (7) forms a first connection (13) which is prestressed at least in relation to an axial direction (11, 12) with a connection element (10) connected to the secondary side (6), the first connection (13) having two opposite surfaces (14, 15) that run inclined in the axial direction (11, 12), the absorber system (7) having a first surface (14) and the connecting element (10) having a second surface (15), the first surface (14 ) and thus the absorber system (7) is pushed along a first axial direction (11) onto the second surface (15) and towards the damping device (3) as a result of the pretension. Torsional vibration damper (1). claim 1 , each surface (14, 15) forming a conical surface which extends along the circumferential direction (8) and along the axial direction (11, 12) with respect to the axial direction (11, 12) is inclined. Torsional vibration damper (1) according to one of the preceding claims, wherein the absorber system (7) is connected to the connecting element (10) via a bayonet connection (16). Torsional vibration damper (1). claim 3 , wherein the bayonet connection (16) is formed by a first disc spring (17) and the connecting element (10). Torsional vibration damper (1). claim 4 , wherein the first plate spring (17) has a first edge region (19) pointing inwards in a radial direction (18) opposite a second axial direction (12) opposite the first axial direction (11) on the connecting element (10) and with an outwardly pointing second edge region (20) opposite the first axial direction (11) on the absorber system (7). Torsional vibration damper (1). claim 5 , wherein the connecting element (10) extends from a first end (21) arranged on the secondary side (6) along the axial direction to a second end (22), the connecting element (10) extending along the second end (22). the circumferential direction (8) has a plurality of first openings (23), wherein along the radial direction (18) through each first opening (23) two extensions (24, 25) of the first disc spring forming the first edge region (19). (17), each extension (24, 25) forming a form-fitting connection with one side surface (26) of the first opening (23) in relation to the circumferential direction (8) and a first extension (24) extending in relation to the second axial direction ( 12) on the connecting element (10) is supported. Torsional vibration damper (1) according to one of the preceding claims, wherein the friction connection (9) is formed by a friction ring (27) extending along the circumferential direction (8), the friction ring (27) being arranged on the damping device (3) and opposite the primary side (5) is freely movable at least along the axial direction (11, 12). Torsional vibration damper (1). claim 7 , wherein the friction ring (27) is opposite to a second axial direction (12) opposite to the first axial direction (11) on the absorber system (7) and opposite to the first axial direction (11) on a spring element (28) and above that on the Secondary side (6) is supported, the friction ring (27) being prestressed via the spring element (28) in relation to the absorber system (7) and the axial direction (11, 12). Torsional vibration damper (1) according to one of the preceding claims, wherein the friction ring (27) has an annular base body (29) and along the circumferential direction (8) a plurality of, starting from the base body (29) along the axial direction (11, 12) extending elevations (30), at least one elevation (30) extending along the axial direction (11, 12) through a second opening (41) in the primary side (5) towards the absorber system (7), so that the friction ring (27 ) is arranged in a form-fitting manner on the primary side (5) relative to the circumferential direction (8). Method for assembling a torsional vibration damper (1) according to one of the preceding claims, at least comprising the following steps: a) providing the damping device (3) as a pre-assembly group, the connecting element (10) being connected to the secondary side (6) of the damping device (3). is; wherein the connecting element (10) extends from one of the secondary side (6) arranged first end (21) along the axial direction (11, 12) towards a second end (22), wherein the conn ment element (10) at the second end (22) along the circumferential direction (8) has a plurality of first openings (23); b) providing the absorber system (7) as a subassembly; c) pushing the absorber system (7) onto the connecting element (10) via the second end (22); d) arranging a first plate spring (17) on the absorber system (7), the first plate spring (17) having a second edge region (20) pointing outwards in a radial direction (18) opposite the first axial direction (11) on the absorber system (7) is supported; wherein the first plate spring (17) along the circumferential direction (8) has a plurality of two extensions (24, 25) each forming a first edge region (19) pointing inwards in the radial direction (18); e) elastic deformation of a first extension (24) in each case, so that the first extension (24) is displaced into the connecting element (10) via the first opening (23) and f) twisting of the first plate spring (17) relative to the connecting element ( 10) so that in each case the second extension (25) is also displaced via the first opening (23) into the connecting element (10) and a bayonet connection (16) and the first connection (13) are formed; Each of the two extensions (24, 25) forming a form-fitting connection with respect to the circumferential direction (8) with a respective side surface (26) of the first opening (23) and the first extension (24) being opposite to one of the first axial direction (11) opposite second axial direction (12) at the second end (22) of the connecting element (10) is supported.

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