DE102022111012A1 - AXIAL LOCKING COMPONENT FOR A ROLLER ORGAN OR AXIAL LOCKING DEVICE - Google Patents

Abstract

The invention relates to a damping device (1) for a drive train, comprising:- a primary flywheel (2) with a central hub (29) which can be connected to a drive shaft, and a secondary flywheel (3) rotating about an axis ( X) are rotatable relative to each other,- a torsion damper (4) made up of elastic members (40) for torque transmission and for damping rotational irregularities between the primary flywheel (2) and the secondary flywheel (3),- a pre-assembled torque limiter (5) which comprising: a torque input member (5A) housing the elastic members (40), a torque output member (5B) connected to the secondary flywheel (3) and at least one sealing washer (58) fixed to the output member (5B), the torque limiter (5) comprising a locking component (9) selected from the output member (52, 53) and the sealing washer (58) and having an additional end (90), de whose shape is adapted by deformation or removal of material of the locking component to accommodate a rolling element (6) or an axial locking device (6'), the secondary flywheel (3) being guided on the primary flywheel (2):- with the rolling element (6), which is partially mounted in the secondary flywheel (3) and held axially: on the one hand by the secondary flywheel (3) and on the other hand by the additional end (90) of the locking component (9),or- with the axial locking device (6'), which on the one hand bears axially at the additional end (90) of the locking component and on the other hand firmly attached to the primary flywheel (2) via retaining means (60', 60").

Description

The invention relates to the field of transmission chains for a mobility machine, such as a truck, an agricultural vehicle, a public transport vehicle or even a hybrid vehicle.

The invention relates to a damping device, such as a damping flywheel, also comprising a rolling element and a torque limiter. The invention also relates to a method for manufacturing such a torque limiter.

In the field of automotive torque transmission, torque transmission devices are known which comprise a primary input flywheel and a secondary output flywheel which are rotatable about a common axis of rotation and are coupled by elastic damping means. These torque-transmitting devices, also known as torsional dampers, allow torque to be transmitted from the engine to the vehicle wheels while absorbing and dampening the vibrations and acyclic movements generated by an internal combustion engine.

Torsion dampers of this type are installed in particular in dual-mass flywheels, in clutch brakes in manual or automated transmissions or in locking clutches in automatic transmissions, also known as “lock-up” clutches, with which devices for hydraulic coupling are equipped. In addition, torque limiters, each consisting of a central cover that accommodates damping springs, can equip such dual-mass flywheels, in particular, to absorb shocks.

Each torque limiter is rotatably attached to the primary flywheel and fixed to the secondary flywheel, generally by a riveted connection. Such a riveted assembly is bulky in the axial direction and prevents the flywheels from approaching each other. There is a risk that such a cover will break under over-torque conditions and that undesirable noise and noise pollution will result. There is thus a need to make this torsional damper assembly more rigid in order to protect the secondary hub of the secondary flywheel, particularly when assembled on the engine side.

In addition, the primary flywheel and the secondary flywheel are connected by a bearing, e.g. B. a rolling bearing, which is arranged between a primary hub of the primary flywheel and a secondary hub of the secondary flywheel, rotatably mounted to each other, so that a relative deflection between these flywheels is made possible.

To be held in position on the secondary flywheel, the roller bearing is axially locked between an inner shoulder of the secondary hub and an axial locking component, such as a locking ring. This resilient locking ring is manually installed in a circular groove formed on an inside of the secondary hub.

The assembly of such bearings between the primary flywheel and the secondary flywheel is in the documents EP2886907 A1 or FR3011602 A1 shown, but this has disadvantages, such as a high number of parts.

In addition, the circular groove requires precise machining to ensure that the locking ring is stably and reliably held in position on the output member hub. This complicates both the manufacture of the circular groove and the positioning of the locking ring on the bearing and in the circular groove. The steps for assembling the bearing to each element are complex and require delicate, time-consuming and costly assembling accuracy.

In addition, the ring may expand or misalign during a skidding motion, or the uneven distribution of contact pressures on its linear form tends to deform it. These errors are incompatible with good axial support of the bearing.

There is a need to develop damping devices with a simple structure that are easy and quick to assemble and to ensure the durability of such components, e.g., the ring and the torque limiter.

The object of the present invention is to at least largely solve the above problems and, moreover, to lead to further advantages.

• - ein Primärschwungrad mit einer mittleren Nabe, das mit einer Antriebswelle verbunden sein kann, und ein Sekundärschwungrad, die um eine Achse X zueinander drehbar sind,
• - einen Torsionsdämpfer aus elastischen Organen zur Übertragung eines Drehmoments und zur Dämpfung der Drehungleichförmigkeiten zwischen dem Primärschwungrad und dem Sekundärschwungrad,
• - einen vormontierten Drehmomentbegrenzer, der Folgendes aufweist:
  • ein Drehmomenteingangsorgan, das die elastischen Organe aufnimmt,
  • ein Drehmomentausgangsorgan, das mit dem Sekundärschwungrad verbunden ist, und
  • mindestens eine Dichtungsscheibe, die fest am Ausgangsorgan angesetzt ist,
  • wobei der Drehmomentbegrenzer eine Arretierkomponente aufweist, die aus dem Ausgangsorgan und der Dichtungsscheibe ausgewählt ist und ein zusätzliches Ende aufweist, dessen Form durch Verformung oder Entfernen von Material von der Arretierkomponente zur Aufnahme eines Rollorgans oder einer Axialarretiervorrichtung angepasst ist,
  • wobei das Sekundärschwungrad auf dem Primärschwungrad geführt ist:
• - mit dem Rollorgan, das teilweise im Sekundärschwungrad angebracht und axial gehalten ist: einerseits durch das Sekundärschwungrad und andererseits durch das zusätzliche Ende der Arretierkomponente,

oder

• - mit der Axialarretiervorrichtung, die fest am Primärschwungrad angebracht ist und einerseits das zusätzliche Ende der Arretierkomponente und andererseits das Sekundärschwungrad axial hält.

The invention first proposes a damping device for a drive train, which has the following:

• - a primary flywheel with a central hub, which can be connected to a drive shaft, and a secondary flywheel, which are mutually rotatable about an axis X,
• - a torsional damper composed of elastic members for torque transmission and to dampen torsional irregularities between the primary flywheel and the secondary flywheel,
• - a pre-assembled torque limiter containing:
  • a torque input organ that houses the elastic organs,
  • a torque output member connected to the secondary flywheel, and
  • at least one sealing washer firmly attached to the output member,
  • the torque limiter having a locking component selected from the output member and the sealing washer and having an additional end whose shape is adapted by deformation or removal of material from the locking component to receive a rolling member or an axial locking device,
  • where the secondary flywheel is guided on the primary flywheel:
• - with the rolling element partially mounted in the secondary flywheel and held axially: on the one hand by the secondary flywheel and on the other hand by the additional end of the locking component,

or

• - with the axial locking device fixed to the primary flywheel and axially holding on the one hand the additional end of the locking component and on the other hand the secondary flywheel.

• - ein Primärschwungrad mit einer mittleren Nabe, das mit einer Antriebswelle verbunden sein kann, und ein Sekundärschwungrad, die um eine Achse X zueinander drehbar sind,
• - einen Torsionsdämpfer aus elastischen Organen zur Übertragung eines Drehmoments und zur Dämpfung der Drehungleichförmigkeiten zwischen dem Primärschwungrad und dem Sekundärschwungrad,
• - einen vormontierten Drehmomentbegrenzer, der Folgendes aufweist:
  • - ein Drehmomenteingangsorgan, das die elastischen Organe aufnimmt,
  • - ein Drehmomentausgangsorgan, das mit dem Sekundärschwungrad verbunden ist, und
  • - mindestens eine Dichtungsscheibe, die fest am Ausgangsorgan angesetzt ist,

wobei das Sekundärschwungrad mit einer Axialarretiervorrichtung auf dem Primärschwungrad geführt ist, die fest am Primärschwungrad angebracht ist und
einerseits das zusätzliche Ende der Arretierkomponente und
andererseits das Sekundärschwungrad axial hält,
wobei die Arretierkomponente des Drehmomentbegrenzers aus dem Ausgangsorgan und der Dichtungsscheibe ausgewählt wird, wobei das zusätzliche Ende der Arretierkomponente durch Materialverformung und/oder Entfernen von Material hergestellt ist.According to a first aspect, the invention proposes a damping device for a drive train, comprising:

• - a primary flywheel with a central hub, which can be connected to a drive shaft, and a secondary flywheel, which are mutually rotatable about an axis X,
• - a torsional damper composed of elastic members for torque transmission and to dampen torsional irregularities between the primary flywheel and the secondary flywheel,
• - a pre-assembled torque limiter containing:
  • - a torque input member that houses the elastic members,
  • - a torque output member connected to the secondary flywheel, and
  • - at least one sealing washer firmly attached to the output member,

the secondary flywheel being guided on the primary flywheel with an axial locking device fixedly attached to the primary flywheel and
on the one hand the additional end of the locking component and
on the other hand holds the secondary flywheel axially,
wherein the locking component of the torque limiter is selected from the output member and the sealing washer, the additional end of the locking component being made by material deformation and/or material removal.

In this way, the axial locking is then realized despite a very narrow axial installation space. It is possible to protect the secondary flywheel and in particular the secondary hub when they are assembled towards the front connected to the engine. The axial locking is formed jointly by the additional axial locking device and one of the pre-assembled components of the torque limiter, which is integral with the secondary flywheel. This avoids complicated post-processing changes (re-machining) both to form the axial detent and to make the circular contours of the secondary flywheel acceptable.

• - ein Primärschwungrad mit einer mittleren Nabe, das mit einer Antriebswelle verbunden sein kann, und ein Sekundärschwungrad, die um eine Achse X zueinander drehbar sind,
• - einen Torsionsdämpfer aus elastischen Organen zur Übertragung eines Drehmoments und zur Dämpfung der Drehungleichförmigkeiten zwischen dem Primärschwungrad und dem Sekundärschwungrad,
• - einen vormontierten Drehmomentbegrenzer, der Folgendes aufweist:
  • - ein Drehmomenteingangsorgan, das die elastischen Organe aufnimmt,
  • - ein Drehmomentausgangsorgan, das mit dem Sekundärschwungrad verbunden ist, und
  • - mindestens eine Dichtungsscheibe, die fest am Ausgangsorgan angesetzt ist,
  wobei das Sekundärschwungrad mit einem Rollorgan auf der mittleren Nabe des Primärschwungrads geführt ist, das teilweise im Sekundärschwungrad angebracht, wobei das Rollorgan axial gehalten ist:
  • einerseits durch das Sekundärschwungrad und
  • andererseits durch ein zusätzliches Ende einer Arretierkomponente des Drehmomentbegrenzers,

wobei die Arretierkomponente des Drehmomentbegrenzers aus dem Ausgangsorgan und der Dichtungsscheibe ausgewählt wird, wobei das zusätzliche Ende der Arretierkomponente durch Materialverformung und/oder Entfernen von Material hergestellt ist.According to a second aspect, the invention proposes a damping device for a drive train, comprising:

• - a primary flywheel with a central hub, which can be connected to a drive shaft, and a secondary flywheel, which are mutually rotatable about an axis X,
• - a torsional damper composed of elastic members for torque transmission and to dampen torsional irregularities between the primary flywheel and the secondary flywheel,
• - a pre-assembled torque limiter containing:
  • - a torque input member that houses the elastic members,
  • - a torque output member connected to the secondary flywheel, and
  • - at least one sealing washer firmly attached to the output member,
  the secondary flywheel having a rolling member on the center hub of the primary flywheel, which is partially mounted in the secondary flywheel, with the rolling element held axially:
  • on the one hand by the secondary flywheel and
  • on the other hand by an additional end of a locking component of the torque limiter,

wherein the locking component of the torque limiter is selected from the output member and the sealing washer, the additional end of the locking component being made by material deformation and/or material removal.

By selecting the locking component from the output member and the sealing washer, the torque limiter directly causes the axial locking of the rolling member without the addition of additional parts, such as a locking ring, to hold the rolling member in abutment with the secondary flywheel.

In addition, the axial detent is formed beforehand by one of the pre-assembled components of the torque limiter, which is then rigidly connected to the secondary flywheel. This avoids complex post-processing changes (re-machining) both to form the axial detent and to make the circular contours of the secondary flywheel acceptable.

The assembly of the damping device is simplified, overall it has a simple, lightweight structure that can be assembled quickly. In addition, axial locking is easy to achieve from the end of the selected locking component of the governor. Only one material deformation and/or material removal step is required in the manufacture of the governor to produce at its end the special shape known as the additional end, which is thus modified and adapted in order to obtain a more stable and reliable hold of the rolling element is guaranteed. Only the so-called additional end realizes the function of the axial locking. The space requirement is limited. The external contact pressures of the rolling element are advantageously localized. The amount of material forming the free end is limited, e.g., in the form of a small portion compared to the entirety of the locking component.

A rolling element is understood here to mean an element for rotationally guiding the flywheels of the damping device, in particular for its hub. The term rolling element includes both plain bearings, which in particular have only a single ring, and roller bearings with an inner and outer ring.

A locking component is to be understood here as an element that is included in the composition of the torque limiter and, in particular, performs a specific function. The term component or element encompasses both a single part performing a function of its own and a group of parts connected in series and performing a common function.

• - Das Rollorgan kann ein Kugellager sein, z.B. ein Schrägkugellager;
• - Das Rollorgan kann ein Nadellager sein;
• - Der Außendurchmesser des Rollorgans kann durch Abstützen des Sekundärschwungrads einerseits und eines zusätzlichen Endes einer Arretierkomponente des Drehmomentbegrenzers andererseits axial gehalten werden;
• - Das zusätzliche Ende kann sich winkelmäßig durchgehend um die Achse X erstrecken. Als Beispiel kann das zusätzliche Ende über 360 Grad um die Achse X einen Kragen oder eine Zentrierschulter bilden;
• - Das zusätzliche Ende kann sich winkelmäßig diskontinuierlich um die Achse X erstrecken. Als Beispiel kann das zusätzliche Ende aus mehreren Axialarretiersegmenten gebildet sein, die um die Achse X verteilt sind;
• - Eine derartige diskontinuierliche Form kann durch Schneiden des zusätzlichen Endes hergestellt werden;
• - Das zusätzliche Ende kann durch Schneiden und/oder Bearbeiten der Arretierkomponente gebildet werden;
• - Das Schneiden kann beispielsweise in Form von Einschnitten erfolgen, wobei die Anzahl der Einschnitte z.B. größer oder gleich drei ist. Unter „Einschnitt“ ist eine Öffnung mit einer Kontur des offenen Typs zu verstehen;
• - Das zusätzliche Ende kann aus mehreren beabstandeten Arretiersegmenten bestehen. Die Anzahl der Arretiersegmente bzw. Einschnitte kann zwischen zwei und zwanzig, vorzugsweise zwischen drei und fünfzehn, betragen;
• - Bei diesen Arretiersegmenten kann es sich um Vorsprünge, Nasen, Laschen oder Lappen zur axialen Arretierung handeln;
• - Diese Arretiersegmente können identische oder unterschiedliche Abmessungen haben;
• - Die Arretiersegmente können in gleichen Abständen oder in einer gleichmäßigen Winkelverteilung angeordnet sein;
• - Die Arretiersegmente können ferner durch Schneiden der Arretierkomponente hergestellt werden;
• - Das zusätzliche Ende kann durch Tiefziehen oder Biegen der Arretierkomponente hergestellt werden:
• - z.B. aus einem Blech des Drehmomentbegrenzers, das die Arretierkomponente bildet;
• - alternativ aus den Köpfen von Befestigungsnieten des Drehmomentbegrenzers, der die Arretierkomponente bildet;

Such a damping device as described above can have one or the other of the features described below, which can be combined with one another or used independently of one another:

• - The rolling element can be a ball bearing, for example an angular ball bearing;
• - The rolling element can be a needle bearing;
• the outside diameter of the rolling element can be kept axial by supporting the secondary flywheel on the one hand and an additional end of a locking component of the torque limiter on the other;
• - The additional end can extend angularly continuously around the X axis. As an example, the additional end can form a collar or centering shoulder over 360 degrees about the X axis;
• - The additional end may extend angularly discontinuously around the X axis. As an example, the additional end can be made up of several axial locking segments distributed around the axis X;
• - Such a discontinuous shape can be made by cutting the extra end;
• - The additional end can be formed by cutting and/or machining the locking component;
• The cutting can be done, for example, in the form of incisions, the number of incisions being greater than or equal to three, for example. “Incision” means an opening with an open-type contour;
• - The additional end can consist of several spaced locking segments. The number of locking segments or incisions can be between two and twenty, preferably between three and fifteen;
• - These locking segments can be protrusions, lugs, tabs or tabs for axial locking;
• - These locking segments can have identical or different dimensions;
• - The locking segments can be arranged at equal intervals or in a uniform angular distribution;
• - The locking segments can also be made by cutting the locking component;
• - The extra end can be made by deep drawing or bending the locking component:
• - eg from a sheet metal of the torque limiter, which forms the locking component;
• - alternatively from the heads of fastening rivets of the torque limiter forming the locking component;

• - Das zusätzliche Ende kann durch Kaltumformung hergestellt werden, insbesondere durch Eindrücken;
• - Dieses Eindrücken kann mit einem Kaltumformungswerkzeug durchgeführt werden;
• - Dieses Eindrücken kann ausgehend von der Bohrung oder der Innenkontur der Arretierkomponente erfolgen;
• - Diese Materialeindrückung kann größer sein als die ursprüngliche Dicke der Arretierkomponente, wobei der Vorteil darin besteht, dass ein Materialabschnitt gebildet wird, der zur übrigen Komponente axial versetzt ist. Das zusätzliche Ende wird dann axial versetzt zur übrigen Arretierkomponente hergestellt, z.B. in einer gebogenen Form;
• - Die Arretierkomponente kann radial verlängert sein, um das zusätzliche Ende durch Materialverlängerung zu bilden. Durch eine derartige Materialverlängerung kann das zusätzliche Ende radial vorstehen;
• - Als Beispiel kann das zusätzliche Ende eine gebogene oder die Form eines Nietkopfes haben;
• - Vorteilhafterweise kann der Drehmomentbegrenzer mit dem zusätzlichen Ende eine innere Aufnahme begrenzen, in der das Rollorgan oder die Axialarretiervorrichtung zumindest teilweise aufgenommen ist. Auf diese Weise wird der Platzbedarf begrenzt;
• - Die Aufnahme kann teilweise durch das Ausgangsorgan des Drehmomentbegrenzers begrenzt sein. Der Vorteil dieses Organs besteht darin, dass es das Rollorgan oder die Axialarretiervorrichtung innerhalb einer Aufnahme teilweise umgibt und enthält, so dass deren Halt und Zentrierung gewährleistet sind;
• - Die Aufnahme kann über 360 Grad um die Achse X ausgebildet sein;
• - Die Aufnahme kann von einem Teil oder einem Ende des Sekundärschwungrads begrenzt sein;
• - Als Variante kann die Aufnahme ein inneres Ende des Sekundärschwungrads enthalten, z.B. das seiner Nabe;
• - Das Eingangsorgan des Drehmomentbegrenzers kann ein einziges mittleres Fenster, Innenbohrung genannt, aufweisen, in dem das Ausgangsorgan des Drehmomentbegrenzers teilweise angebracht ist. Außerdem kann das Ausgangsorgan des Drehmomentbegrenzers ein einziges mittleres Fenster, Innenbohrung genannt, aufweisen, in der das Rollorgan oder die Axialarretiervorrichtung teilweise angebracht ist. Mit anderen Worten können das Ausgangsorgan einerseits und das Rollorgan oder die Axialarretiervorrichtung andererseits radial übereinander angeordnet sein. Der Vorteil derartiger Eingangs- und Ausgangsorgane besteht darin, dass sie radial ausgerichtet und insbesondere in derselben Ebene senkrecht zur Achse X enthalten sind. Auf diese Weise wird der Platzbedarf begrenzt;
• - Vorteilhafterweise kann das zusätzliche Ende einen Hohlraum aufweisen, der die innere Aufnahme teilweise begrenzt und in dem das Rollorgan oder die Axialarretiervorrichtung zumindest teilweise aufgenommen ist;
• - Die Aufnahme, und insbesondere der Hohlraum, kann durch Entfernen von Material aus dem zusätzlichen Ende hergestellt werden;
• - Dieses Entfernen von Material kann auf zwischen 2/3 und 9/10 der ursprünglichen Dicke des zusätzlichen Endes, d. h. der ursprünglichen Dicke der Arretierkomponente, an dem das zusätzliche Ende ausgebildet ist, durchgeführt werden. Hier wird das Material, das zur Herstellung des zusätzlichen Endes und der Aufnahme benötigt wird, auf ein Minimum reduziert.
• - Dieses Entfernen von Material kann durch maschinelle Bearbeitung erfolgen. Der Bearbeitungsschritt ermöglicht es, innerhalb der Aufnahme eine ebene Abstützung zu definieren und zu lokalisieren, an der sich das Rollorgan oder die Axialarretiervorrichtung axial abstützt;
• - Die Aufnahme, und insbesondere der Hohlraum, kann eine Fläche zur axialen Abstützung aufweisen;
• - Die Fläche zur axialen Abstützung des Gehäuses und insbesondere des Hohlraums kann kontinuierlich oder alternativ diskontinuierlich um die Achse X sein;
• - Die diskontinuierliche Fläche zur axialen Abstützung kann durch beabstandete Arretiersegmente gebildet sein;
• - Die diskontinuierliche Fläche zur axialen Abstützung des Gehäuses und insbesondere des Hohlraums kann durch Schneiden und/oder maschinelle Bearbeitung hergestellt werden;
• - Die diskontinuierliche Fläche zur axialen Abstützung kann durch Kaltumformung, durch Tiefziehen hergestellt werden;
• - Außerdem kann das zusätzliche Ende und insbesondere der Hohlraum eine Zentrierauflage aufweisen;
• - Die Zentrierauflage kann zylindrisch sein und eine kontinuierliche oder diskontinuierliche Form um die Achse X haben;
• - Das Drehmomenteingangsorgan kann eine Mitnehmerscheibe sein, die die elastischen Organe aufnehmen kann;
• - Das Drehmomentausgangsorgan kann zwei Sicherungshalter aufweisen, die fest miteinander verbunden sind und mit dem Drehmomenteingangsorgan zusammenwirken. Durch die Herstellung des Ausgangsorgans aus mehreren Teilen wird seine Festigkeit verbessert, so dass es den Stützbeanspruchungen des Eingangsorgans besser standhält, und dabei wird eine geringe Trägheit gewährleistet, die im Betrieb keine Resonanzen oder Lärmbelästigung erzeugt;
• - Der Innendurchmesser der Mitnehmerscheibe kann größer sein als der Innendurchmesser des Drehmomentausgangsorgans, insbesondere 1,3-mal größer als der Innendurchmesser der Sicherungshalter. Der Durchmesserunterschied gewährleistet eine gleichmäßige Übertragung des Antriebsmoments, z.B. mit einem Rutschmoment, das mindestens dem Doppelten des maximalen Antriebsmoments entspricht;
• - Die Mitnehmerscheibe kann eine flexible oder elastische Scheibe vom Typ Belleville sein. Dadurch wird das Risiko eines Bruchs und einer Beschädigung des Eingangsorgans des Drehmomentbegrenzers weiter verringert. Der Vorteil einer derartigen Mitnehmerscheibe besteht darin, dass durch Reibschluss mit den Sicherungshaltern eine wesentlich höhere Last aufgebracht wird, so dass verhindert wird, dass die Mitnehmerscheibe vor einem bestimmten vorgegebenen Drehmoment rutscht;
• - Die Sicherungshalter können axial auf der einen und auf der anderen Seite des Drehmomenteingangsorgans angeordnet sein;
• - Das Drehmomenteingangsorgan, und insbesondere die Mitnehmerscheibe, kann axial zwischen den Sicherungshaltern gehalten sein. Die Mitnehmerscheibe und die Sicherungshalter können einen axialen Stapel bilden. Da die beiden Sicherungshalter die Mitnehmerscheibe auf der einen und auf der anderen Seite halten, haben diese einen einfachen Aufbau und tragen am meisten zur axialen Belastung der Baugruppe bei. Dieser vormontierte Stapel verhindert daher den Bruch der Mitnehmerscheibe unter Bedingungen mit einem übermäßigen Drehmoment.
• - Mit anderen Worten können die Sicherungshalter einen Freiraum begrenzen, in dem das Eingangsorgan aufgenommen ist. Im zusammengebauten Zustand kann die Mitnehmerscheibe unabhängig zwischen den Halteschalen gleiten, insbesondere ab einem bestimmten vorgegebenen Drehmoment;
• - Die Sicherungshalter können einen Boden begrenzen, in dem die Mitnehmerscheibe in Anlage gelangt;
• - Die Sicherungshalter können die Form eines Bogens, einer Schale, eines Endstücks oder eines Zapfens oder jede andere Form eines Teils haben, dessen Ende für eine Verbindung, insbesondere mit dem Drehmomenteingangsorgan, vorbereitet ist;
• - Die Sicherungshalter können unterschiedliche Außendurchmesser haben, wobei der Vorteil darin besteht, dass sie unterscheidbar sind und die Montage des Drehmomentbegrenzers vereinfacht wird. Es wird sichergestellt, dass sie sich in der richtigen Position zum Sekundärschwungrad befinden;
• - Als Beispiel kann der Sicherungshalter mit dem kleineren Außendurchmesser (unterer Halter genannt) auf der Motorseite, insbesondere auf der Seite des Primärschwungrads, insbesondere so weit wie möglich von dem Sekundärschwungrad entfernt angeordnet sein;
• - Der Sicherungshalter mit dem größten Außendurchmesser (oberer Halter genannt) kann beispielsweise auf der Getriebeseite, insbesondere so nah wie möglich am Sekundärschwungrad angeordnet sein;
• - Die Sicherungshalter können für die Anbringung der Mitnehmerscheibe, insbesondere entsprechend einer Montage mit Anschlag, jeweils ein Stützmittel aufweisen, das einstückig im Inneren der Halter ausgebildet ist;
• - Diese Stützmittel können gemeinsam den Boden der Sicherungshalter, mit anderen Worten den Freiraum begrenzen, in dem die Mitnehmerscheibe in Kontakt gelangt, insbesondere mit radialer Abstützung;
• - Mindestens ein Stützmittel eines Sicherungshalters kann eine Schulter mit einer ebenen axialen Fläche sein, mit anderen Worten eine Falte senkrecht zum übrigen Sicherungshalter;
• - Mindestens ein Stützmittel eines Sicherungshalters kann eine ebene axiale Fläche sein, die durch einen oder mehrere tangentiale Prägungen hergestellt wird. Ein besserer Kontaktbereich ist zwischen den Haltern und der Mitnehmerscheibe möglich, so dass die Scheibe parallel zu den Sicherungshaltern ausgerichtet ist. Die Mitnehmerscheibe und insbesondere deren Finger sind dann konzentrisch zu den anderen Komponenten des Drehmomentbegrenzers. Dadurch wird ein unerwünschter Kontakt oder ein vorzeitiges Versagen der Komponenten (das sich aus einer Fehlausrichtung ergeben würde) vermieden;
• - Die ebene axiale Fläche kann kontinuierlich oder alternativ diskontinuierlich um die Achse X sein. Die ebene axiale Fläche kann eine Gruppe von eingedrückten Abschnitten sein, die winkelmäßig voneinander beabstandet sind;
• - Die Sicherungshalter können ab einem definierten Drehmomentwert reibschlüssig mit der Mitnehmerscheibe zusammenwirken, so dass das Gleiten der Mitnehmerscheibe durch Reibung an jedem der Sicherungshalter gesteuert werden kann. Dadurch wird das Risiko eines Bruchs oder einer Beschädigung bei einem übermäßigen Drehmoment begrenzt;
• - Jeder der Sicherungshalter kann einen Reibungsbereich definieren, der mit dem Drehmomenteingangsorgan zusammenwirkt;
• - Die Reibungsbereiche können auf einer der Seitenflächen jedes der Sicherungshalter begrenzt werden;
• - Ein Reibungsbereich kann sich ausgehend von dem Außendurchmesser eines der Sicherungshalter erstrecken;
• - Insbesondere kann sich jeder Reibungsbereich ausgehend von dem Außendurchmesser der Sicherungshalter erstrecken;
• - Jeder Reibungsbereich kann eine Reibungsvorrichtung und insbesondere Reibbeläge aufweisen;
• - Die Sicherungshalter können Reibbeläge aufweisen, die axial gegenüber den Seitenflächen des Drehmomenteingangsorgans angeordnet sind;
• - Als Beispiel kann mindestens einer der Reibbereiche mit dem Innendurchmesser der Mitnehmerscheibe zusammenwirken, so dass die Mitnehmerscheibe durch Verklemmen im Inneren des Sicherungshalters gehalten ist;
• - Als Beispiel kann mindestens einer der Reibbereiche mit dem Außendurchmesser der Mitnehmerscheibe zusammenwirken. Die Reibung wirkt dann in verschiedenen getrennten und voneinander beabstandeten Bereichen der Mitnehmerscheibe;
• - Die Reibbeläge können aus verschiedenen Reibmaterialien ausgewählt sein, einschließlich Papier und/oder Graphitbeschichtung. Die Reibbeläge können an jedem der Sicherungshalter angebracht sein, z.B. durch Kleben oder andere Verbindungsmittel, als Variante durch Vernieten;
• - Die Reibbeläge können segmentiert oder als Variante winkelmäßig kontinuierlich um die Achse X sein;
• - Darüber hinaus kann das Drehmomentausgangsorgan eine Beilagscheibe aufweisen, die sich an einem der Sicherungshalter abstützt, z B. an einer ihrer Seitenflächen. Die Beilagscheibe kann elastisch oder starr sein;
• - Die Beilagscheibe kann zwischen dem Ende der ersten Befestigungsmittel und einem der Sicherungshalter angeordnet sein. Genauer gesagt kann die Beilagscheibe zwischen dem Kopf der Nieten, die die ersten Befestigungsmittel bilden, und einem der Sicherungshalter angeordnet sein;
• - Die Beilagscheibe kann eine kontinuierliche oder segmentierte Form um die Achse X haben;
• - Die Beilagscheibe kann aus mehreren Blechschichten, z.B. zwei Blechschichten bestehen;
• - Diese Blechschichten, die die Beilagscheibe bilden, können insbesondere durch Schneiden segmentiert werden;
• - Die Eingangs- und Ausgangsorgane des Drehmomentbegrenzers können über erste Befestigungsmittel, insbesondere über eine Reihe von Befestigungsschrauben, -bolzen oder -nieten zusammengefügt sein. Insbesondere können die Dichtungsscheibe und die Sicherungshalter über die ersten Befestigungsmittel fest miteinander verbunden sein.

This material deformation produces a deep-drawn or curved shape that is suitable for receiving the rolling element or the axial locking device. Here, deep-drawing enables the cost-effective production of complex shapes. A component is formed from a deep-drawn sheet metal and performs several functions, including axial locking and torque limitation;

• - The additional end can be made by cold forging, in particular by pressing;
• - This indentation can be done with a cold forming tool;
• - This pressing can be done starting from the hole or the inner contour of the locking component;
• This indentation of material can be greater than the original thickness of the locking component, the advantage being that a portion of material is formed which is axially offset to the rest of the component. The extra end is then fabricated axially offset from the rest of the locking component, eg in a curved shape;
• - The locking component can be extended radially to form the additional end by material extension. Such a lengthening of the material allows the additional end to protrude radially;
• - As an example, the additional end can have a curved or the shape of a rivet head;
• Advantageously, with the additional end, the torque limiter can delimit an internal housing in which the rolling member or the axial locking device is at least partially housed. In this way, the space required is limited;
• - The absorption can be partly limited by the output device of the torque limiter. The advantage of this member is that it partially surrounds and contains the rolling member or the axial locking device within a housing, ensuring that it is held and centered;
• - The receptacle can be formed over 360 degrees around the axis X;
• - The intake can be limited by a part or an end of the secondary flywheel;
• - As a variant, the housing can contain an inner end of the secondary flywheel, for example that of its hub;
• - The input member of the torque limiter can have a single central window, called an internal hole, in which the output member of the torque limiter is partially fitted. Furthermore, the output member of the torque limiter can have a single central window, called the internal bore, in which the rolling member or the axial locking device is partially mounted. In other words, the output element on the one hand and the rolling element or the axial locking device on the other hand can be arranged radially one above the other. The advantage of such input and output members is that they are radially oriented and in particular contained in the same plane perpendicular to the X axis. In this way, the space required is limited;
• Advantageously, the additional end can have a cavity partially delimiting the internal housing and in which the rolling member or the axial locking device is at least partially housed;
• - The receptacle, and in particular the cavity, can be made by removing material from the additional end;
• - This removal of material can be performed on between 2/3 and 9/10 of the original thickness of the additional end, ie the original thickness of the locking component on which the additional end is formed. Here the material needed to manufacture the extra end and the socket is reduced to a minimum.
• - This removal of material can be done by machining. The machining step makes it possible to define and locate, inside the housing, a plane support against which the rolling element or the axial locking device bears axially;
• the housing, and in particular the cavity, may have an axial bearing surface;
• the axial support surface of the casing and in particular of the cavity may be continuous or, alternatively, discontinuous around the X axis;
• - The discontinuous surface for axial support can be formed by spaced locking segments;
• the discontinuous surface for axial support of the casing and in particular of the cavity can be made by cutting and/or machining;
• - The discontinuous surface for axial support can be made by cold forging, by stamping;
• - In addition, the additional end and in particular the cavity may have a centering pad;
• - The centering pad can be cylindrical and have a continuous or discontinuous shape around the X axis;
• - The torque input member can be a drive plate capable of receiving the elastic members;
• - The torque output member can have two fuse holders which are integral with each other and cooperate with the torque input member. By making the output member in several parts, its strength is increased so that it better withstands the stresses of support of the input member, while ensuring a low inertia that does not generate resonances or noise nuisance during operation;
• - The internal diameter of the drive plate can be larger than the internal diameter of the torque output device, in particular 1.3 times larger than the internal diameter of the fuse holders. The difference in diameter ensures an even transmission of the drive torque, eg with a slip torque that corresponds to at least twice the maximum drive torque;
• - The drive disc can be a flexible or elastic Belleville type disc. This further reduces the risk of breakage and damage to the torque limiter input member. The advantage of such a drive plate is that a significantly higher load is applied by frictional engagement with the fuse holders, so that the drive plate is prevented from slipping before a certain predetermined torque;
• - The fuse holders can be arranged axially on one side and on the other side of the torque input member;
• - The torque input member, and in particular the drive plate, can be held axially between the fuse holders. The drive plate and the fuse holders can form an axial stack. Since the two fuse holders hold the drive plate on one side and the other, they have a simple structure and contribute most to the axial load on the assembly. This pre-assembled stack therefore prevents the drive plate from breaking under excessive torque conditions.
• - In other words, the fuse holders can delimit a space in which the input member is housed. In the assembled state, the drive plate can slide independently between the retaining shells, in particular from a certain predetermined torque;
• - The fuse holders can delimit a floor in which the drive plate comes to rest;
• - The fuse holders can be in the form of an arc, a cup, a terminal or a pin, or any other shape of a part, the end of which is prepared for connection, in particular with the torque input member;
• - The fuse holders can have different external diameters, the advantage being that they are distinguishable and simplifying the assembly of the torque limiter. It is ensured that they are in the correct position in relation to the secondary flywheel;
• As an example, the fuse holder with the smaller external diameter (called the lower holder) can be located on the engine side, in particular on the primary flywheel side, in particular as far as possible from the secondary flywheel;
• - The fuse holder with the largest outside diameter (called the top holder) can be for example on the transmission side, in particular as close as possible to the secondary flywheel;
• the fuse holders can each have a support means formed in one piece inside the holders for the attachment of the drive plate, in particular according to an assembly with stop;
• these support means can jointly delimit the bottom of the fuse holders, in other words the free space in which the drive plate comes into contact, in particular with radial support;
• at least one support means of a fuse holder can be a shoulder with a flat axial face, in other words a fold perpendicular to the rest of the fuse holder;
• - At least one means of support of a fuse holder can be a flat axial surface made by one or more tangential stampings. A better area of contact is allowed between the holders and the drive plate so that the plate is aligned parallel to the fuse holders. The drive plate and in particular its fingers are then concentric with the other components of the torque limiter. This avoids unwanted contact or premature component failure (which would result from misalignment);
• - The planar axial surface can be continuous or alternatively discontinuous around the X axis. The planar axial surface may be a set of indented sections angularly spaced from each other;
• - The fuse holders can interact frictionally with the drive plate from a defined torque value, so that the sliding of the drive plate can be controlled by friction on each of the fuse holders. This limits the risk of breakage or damage from excessive torque;
• - Each of the fuse holders can define a friction area that interacts with the torque input member;
• - The areas of friction can be limited on one of the lateral faces of each of the fuse holders;
• - A friction area may extend from the outside diameter of one of the fuse holders;
• - In particular, each friction zone can extend from the outside diameter of the fuse holders;
• - Each friction area can have a friction device and in particular friction pads;
• the fuse holders may have friction linings arranged axially opposite the lateral faces of the torque input member;
• - As an example, at least one of the friction zones can cooperate with the inside diameter of the drive plate, so that the drive plate is held by wedging inside the fuse holder;
• - As an example, at least one of the friction areas can interact with the outer diameter of the drive plate. The friction then acts in various separate and spaced apart areas of the drive plate;
• - The friction linings can be selected from different friction materials including paper and/or graphite coating. The friction linings can be attached to each of the fuse holders, for example by gluing or other means of connection, as a variant by riveting;
• - The linings can be segmented or, as a variant, angularly continuous around the X axis;
• In addition, the torque output member may include a washer bearing against one of the fuse holders, for example on one of its lateral surfaces. The washer can be flexible or rigid;
• - The washer can be placed between the end of the first fasteners and one of the fuse holders. More precisely, the washer can be placed between the heads of the rivets forming the first fastening means and one of the fuse holders;
• - The washer can have a continuous or segmented shape around the X axis;
• - The washer can consist of several layers of sheet metal, eg two layers of sheet metal;
• - These layers of sheet metal, which form the washer, can be segmented, in particular by cutting;
• The input and output members of the torque limiter can be assembled by first means of attachment, in particular by a series of attachment screws, bolts or rivets. In particular, can the sealing disk and the fuse holder can be firmly connected to one another via the first fastening means.

The preassembly of the torque limiter components forms a preassembled unitary subassembly. The assembly, transport and handling steps of the torque limiter components are simplified. This unified subassembly is cost effective and combines multiple functions including sealing and torque limiting.

• - Der Drehmomentbegrenzer, insbesondere das Drehmomentausgangsorgan, kann über zweite Befestigungsmittel, insbesondere über eine Reihe von Befestigungsschrauben, -bolzen oder -nieten mit dem Sekundärschwungrad verbunden sein;
• - Das Sekundärschwungrad kann eine Montageschnittstelle aufweisen, an der der Drehmomentbegrenzer angebracht ist. Die Montageschnittstelle des Sekundärschwungrads ist dann dazu geeignet, das Drehmomentausgangsorgan aufzunehmen;
• - Die Montageschnittstelle kann an einer sekundären Nabe des Sekundärschwungrads ausgebildet sein;
• - Bei den ersten und zweiten Befestigungsmitteln handelt es sich um zwei verschiedene Reihen von Befestigungsschrauben, -bolzen oder -nieten;
• - Die ersten und zweiten Befestigungsmittel können längs der Achse X voneinander beabstandet sein. Die ersten und zweiten Befestigungsmittel können auf Anordnungskreisen mit unterschiedlichen Durchmessern angeordnet sein;
• - Die mindestens eine Dichtungsscheibe kann sich am Ausgangsorgan abstützen, beispielsweise an der Seitenfläche eines der Sicherungshalter. Die mindestens eine Dichtungsscheibe kann über eine Nietverbindung, mit jedem möglichen Befestigungsmittel mit dem Ausgangsorgan des Drehmomentbegrenzers und/oder mit dem Sekundärschwungrad fest verbunden sein;
• - Die mindestens eine Dichtungsscheibe kann insbesondere mit ersten Befestigungsmitteln mit dem Ausgangsorgan fest verbunden sein. Die Dichtungsscheibe kann insbesondere mit zweiten Befestigungsmitteln mit dem Sekundärschwungrad fest verbunden sein. Vorteilhaft ist es, die Dichtungsscheibe über verschiedene mögliche Befestigungsmittel mit dem Ausgangsorgan einerseits und mit dem Sekundärschwungrad andererseits zu befestigen;
• - Die mindestens eine Dichtungsscheibe kann axial zwischen dem Ausgangsorgan und dem Sekundärschwungrad eingefügt sein. Die mindestens eine Dichtungsscheibe kann ein staubabweisendes Element für die Schwungräder sein;
• - Die Dichtungsscheibe kann zur Gewährleistung der Dichtigkeit des Primär- und Sekundärschwungrads elastisch oder starr sein;
• - Vorteilhafterweise kann die Arretierkomponente durch das Drehmomentausgangsorgan gebildet sein, wobei der Vorteil darin besteht, dass eine Doppelfunktion realisiert wird: die der Drehmomentübertragung, zusätzlich zur axialen Arretierung des Rollorgans oder der Axialarretiervorrichtung;
• - Die Arretierkomponente kann z.B. durch einen der Sicherungshalter gebildet sein;
• - Insbesondere kann die Arretierkomponente durch den Sicherungshalter gebildet sein, der axial am weitesten von dem Sekundärschwungrad entfernt ist, d.h. den Sicherungshalter, der auf der Motorseite angeordnet ist;
• - Das zusätzliche Ende des Sicherungshalters kann durch Materialverformung und/oder Entfernen von Material aus seinem Innendurchmesser hergestellt werden, insbesondere durch Tiefziehen, Biegen und/oder maschinelle Bearbeitung des Sicherungshalters;
• - In einem weiteren Beispiel kann die Arretierkomponente durch die Beilagscheibe gebildet sein;
• - In dieser Situation kann das zusätzliche Ende auf ihrem Innendurchmesser ausgebildet sein;
• - Das zusätzliche Ende kann durch Materialverformung, insbesondere durch Biegen, hergestellt werden;
• - Das zusätzliche Ende kann durch Entfernen von Material, insbesondere durch Schneiden, hergestellt werden;
• - In einem weiteren Beispiel kann die Arretierkomponente durch mindestens einige der ersten Befestigungsmittel gebildet sein. Vorzugsweise können die ersten Befestigungsmittel durch eine Reihe von Nieten gebildet sein. Mit anderen Worten können die Sicherungshalter und die Dichtungsscheibe durch eine Reihe von Nieten miteinander verbunden sein, die erste Befestigungsmittel bilden, bei denen zumindest einige der sogenannten Arretiernieten die Arretierkomponente bilden. Der Vorteil besteht darin, dass eine Doppelfunktion realisiert wird: die der Vormontage der Komponenten des Drehmomentbegrenzers, zusätzlich zur axialen Arretierung des Rollorgans oder der Axialarretiervorrichtung;
• - Das zusätzliche Ende derartiger Arretiernieten kann dann durch Materialverformung, insbesondere durch Materialverlängerung, so hergestellt werden, dass es am Rollorgan oder an der Axialarretiervorrichtung anschlägt;
• - Insbesondere kann das zusätzliche Ende durch Materialverformung des Kopfes der Nieten aus der Reihe hergestellt werden. Anders ausgedrückt, das zusätzliche Ende kann die Form eines Schließkopfes haben;
• - Das zusätzliche Ende derartiger Arretiernieten kann tiefgezogen und/oder maschinell bearbeitet sein;
• - Die Arretierkomponente kann aus Paaren von Arretiernieten bestehen;
• - Insbesondere bildet die gesamte Reihe der Befestigungsnieten die Arretierkomponente;
• - Vorteilhafterweise kann die Arretierkomponente durch die mindestens eine Dichtungsscheibe gebildet sein, so dass eine Doppelfunktion erfüllt wird: die der Abdichtung der Baugruppe, zusätzlich zur axialen Arretierung des Rollorgans. Die Dichtungsscheibe kann sich z.B. an der Innenbohrung der Sicherungshalter abstützen;
• - Das zusätzliche Ende kann durch Materialumformung, durch Tiefziehen oder Biegen hergestellt werden. Die Dichtungsscheibe kann im Ausgangsorgan, insbesondere im Inneren der Sicherungshalter, untergebracht sein;
• - Die Dichtungsscheibe kann das Ausgangsorgan axial durchdringen. Die Dichtungsscheibe kann dann axial auf der einen und auf der anderen Seite des Drehmomentausgangsorgans und insbesondere der Sicherungshalter ausmünden;

For example, the sealing disc can improve lubrication within the torque limiter by acting as an oil deflector, for example to concentrate hydraulic fluid circulation on the friction linings;

• the torque limiter, in particular the torque output member, can be connected to the secondary flywheel by second attachment means, in particular by a series of attachment screws, bolts or rivets;
• - The secondary flywheel may have a mounting interface to which the torque limiter is attached. The secondary flywheel mounting interface is then adapted to receive the torque output member;
• - The mounting interface may be formed on a secondary hub of the secondary flywheel;
• - The first and second fastening means are two different sets of fastening screws, bolts or rivets;
• - The first and second attachment means may be spaced apart along the X axis. The first and second fasteners may be arranged on locating circles of different diameters;
• The at least one washer can bear against the output member, for example against the side surface of one of the fuse holders. The at least one sealing washer can be fixed to the output member of the torque limiter and/or to the secondary flywheel by a riveted connection, by any possible fastening means;
• The at least one sealing disk can be firmly connected to the output member, in particular with first fastening means. The sealing washer can be fixedly connected to the secondary flywheel, in particular with second fastening means. It is advantageous to attach the sealing washer to the output member on the one hand and to the secondary flywheel on the other hand using various possible attachment means;
• The at least one sealing washer can be inserted axially between the output member and the secondary flywheel. The at least one sealing disk can be a dust-repellent element for the flywheels;
• - The sealing washer can be elastic or rigid to ensure the seal of the primary and secondary flywheel;
• Advantageously, the locking component can be constituted by the torque output member, the advantage being that a dual function is achieved: that of torque transmission, in addition to the axial locking of the rolling member or axial locking device;
• - The locking component can be formed, for example, by one of the fuse holders;
• - In particular, the locking component can be constituted by the fuse holder that is axially furthest from the secondary flywheel, ie the fuse holder that is located on the engine side;
• - The additional end of the fuse holder can be made by material deformation and/or removal of material from its inner diameter, in particular by deep drawing, bending and/or machining of the fuse holder;
• - In another example, the locking component can be formed by the washer;
• - In this situation, the extra end can be formed on its inner diameter;
• - The additional end can be made by material deformation, in particular by bending;
• - The additional end can be made by removing material, in particular by cutting;
• - In a further example, the locking component can be formed by at least some of the first fastening means. Preferably, the first fastening means can be formed by a series of rivets. In other words, the fuse holders and the sealing washer can be connected to one another by a series of rivets which form first fastening means, in which at least some of the so-called locking rivets form the locking component. The advantage is that a double function is realized: that of pre-assembling the components of the torque limiter, in addition to the axial locking of the rolling element or the axial locking device;
• - The additional end of such locking rivets can then be made by material deformation, in particular by material elongation, so that it strikes the rolling element or the axial locking device;
• - In particular, the additional end can be made by material deformation of the head of the rivets from the series. In other words, the additional end can be in the form of a closure head;
• - The additional end of such locking rivets may be deep drawn and/or machined;
• - The locking component can consist of pairs of locking rivets;
• - In particular, the entire row of fastening rivets forms the locking component;
• Advantageously, the locking component can be constituted by at least one sealing washer, so that a double function is fulfilled: that of sealing the assembly, in addition to the axial locking of the rolling element. The sealing washer can be supported, for example, on the inner bore of the fuse holder;
• - The additional end can be made by material transformation, by deep drawing or by bending. The sealing washer can be housed in the output member, in particular inside the fuse holders;
• - The sealing washer can penetrate the outlet member axially. The sealing washer can then open out axially on one side and on the other side of the torque output member and in particular the fuse holder;

• - ein Primärschwungrad mit einer mittleren Nabe, das mit einer Antriebswelle verbunden sein kann, und ein Sekundärschwungrad, die um eine Achse X zueinander drehbar sind,
• - einen Torsionsdämpfer, der Folgendes umfasst: elastische Organe zur Übertragung eines Drehmoments und zur Dämpfung der Drehungleichförmigkeiten zwischen dem Primärschwungrad und dem Sekundärschwungrad,
• - einen vormontierten Drehmomentbegrenzer, der Folgendes aufweist:
  • ein Drehmomenteingangsorgan, das die elastischen Organe aufnimmt,
  • ein Drehmomentausgangsorgan, das mit dem Sekundärschwungrad verbunden ist, und
  • mindestens eine Dichtungsscheibe, die fest am Ausgangsorgan angesetzt ist,
  • wobei die Dämpfungsvorrichtung ferner eine Axialarretiervorrichtung aufweist, die aus mindestens einer Hysteresekassette gebildet ist, ausgehend von der das Ausgangsorgan des Drehmomentbegrenzers in Bezug auf das Primärschwungrad geführt ist, wobei die mindestens eine Hysteresekassette durch Mittel zur Verriegelung und zur Zentrierung fest mit dem Primärschwungrad verbunden ist.

According to a third aspect, the invention proposes a damping device for a drive train, which has:

• - a primary flywheel with a central hub, which can be connected to a drive shaft, and a secondary flywheel, which are mutually rotatable about an axis X,
• - a torsional damper comprising: elastic members for torque transmission and for damping torsional irregularities between the primary flywheel and the secondary flywheel,
• - a pre-assembled torque limiter containing:
  • a torque input organ that houses the elastic organs,
  • a torque output member connected to the secondary flywheel, and
  • at least one sealing washer firmly attached to the output member,
  • the damping device also comprising an axial locking device constituted by at least one hysteresis cassette from which the output member of the torque limiter is guided with respect to the primary flywheel, the at least one hysteresis cassette being integral with the primary flywheel by locking and centering means.

The axial locking of the secondary flywheel is improved despite a very narrow axial space between the flywheels. The secondary flywheel is protected when assembled with the primary flywheel on the side connected to the engine.

• - Vorteilhafterweise kann die Axialarretiervorrichtung aus mindestens einem Zentrierstück, vorzugsweise vom Typ Scheibe, bestehen, ausgehend von dem das Drehmomentausgangsorgan des Drehmomentbegrenzers direkt oder indirekt zentriert wird. Dieses Zentrierstück kann über Haltemittel, z. B. Nieten, fest mit dem Primärschwungrad verbunden sein. Alle anderen Verbindungsmittel sind auch möglich;
• - Das Zentrierstück der Axialarretiervorrichtung kann vorzugsweise Folgendes umfassen:
• - eine Zentrierauflage, auf der eine Hysteresekassette radial zentriert ist; oder
• - eine Halteauflage, auf der das Ausgangsorgan des Drehmomentbegrenzers in axialer Anlage positioniert ist.
• - Vorteilhafterweise kann die Axialarretiervorrichtung mindestens einen axialen Stapel von Scheiben aufweisen, die zwischen dem Primärschwungrad oder Sekundärschwungrad einerseits und dem Drehmomentbegrenzer andererseits eingefügt sind.

Such a damping device according to the second or third aspect of the invention can have one or the other of the features described below, which are used in combination with one another or independently of one another:

• Advantageously, the axial locking device can consist of at least one centering piece, preferably of the washer type, from which the torque output member of the torque limiter is centered directly or indirectly. This centering can hold means such. B. rivets, be firmly connected to the primary flywheel. All other means of connection are also possible;
• - The centering piece of the axial locking device may preferably include:
• - a centering pad on which a hysteresis cassette is radially centered; or
• - a support on which the output member of the torque limiter is positioned in axial abutment.
• Advantageously, the axial locking device can comprise at least one axial stack of washers interposed between the primary or secondary flywheel on the one hand and the torque limiter on the other.

This axial stack of washers can include at least one guide washer of the plastic guide washer type.

This axial stack of discs can include at least the centering piece.

• - Alternativ oder in Kombination kann die Axialarretiervorrichtung aus mindestens einer Hysteresekassette bestehen, die aus mindestens einem Führungskäfig und einer Federscheibe gebildet ist. Die mindestens eine Kassette kann zwischen dem Primärschwungrad und dem Drehmomentausgangsorgan des Drehmomentbegrenzers eingefügt sein. Der Führungskäfig kann in axialer Anlage am Drehmomentausgangsorgan des Drehmomentbegrenzers angebracht sein. Die Federscheibe kann in einem Neigungswinkel α1, α2 in Bezug auf den mindestens einen Führungskäfig konisch geformt sein;
• - Beispielsweise kann eine Hysteresekassette der Axialarretiervorrichtung eine Federscheibe aufweisen, die zwischen zwei Führungskäfigen eingefügt ist, die koaxial sind und an Zentrierrändern, die insbesondere axial einander gegenüber angeordnet sind, übereinander angebracht sind. Einer der Führungskäfige kann in einer Materialaussparung des zusätzlichen Endes der Arretierkomponente untergebracht sein. Die beiden Führungskäfige können über Verriegelungsmittel vom Typ Rastmittel miteinander verbunden sein, die komplementär ausgebildet sind;
• - In einem weiteren Beispiel kann eine Hysteresekassette der Axialarretiervorrichtung eine Federscheibe aufweisen, die zwischen einem einzelnen Führungskäfig und einem Deckel des Primärschwungrads eingefügt ist. In einer besonderen Ausführungsform kann dieser Führungskäfig durch den Deckel des Primärschwungrads über eine Zentrierauflage vom Typ Kragen zentriert sein. In einer weiteren besonderen Ausführungsform kann dieser Führungskäfig durch den Deckel gehalten werden, vorzugsweise durch Verriegelungsmittel vom Typ Rastmittel;
• - In einem ersten Beispiel kann die Axialarretiervorrichtung eine Hysteresekassette auf einer axialen Seite des Drehmomentbegrenzers und einen Scheibenstapel auf der anderen axialen Seite des Drehmomentbegrenzers aufweisen. Die Axialarretiervorrichtung kann ferner ein Zentrierstück aufweisen, auf dem entweder die Hysteresekassette oder der Stapel aus Feder- und Kunststoffscheiben in Bezug auf das Primärschwungrad zentriert ist;
• - In einem weiteren Beispiel kann die Axialarretiervorrichtung auf derselben axialen Seite des Drehmomentbegrenzers ein Zentrierstück aufweisen, auf dem ein Stapel aus Feder- und Kunststoffscheiben zentriert ist;
• - In einem weiteren Beispiel kann die Axialarretiervorrichtung auf einer axialen Seite des Drehmomentbegrenzers eine Hysteresekassette und auf der anderen axialen Seite des Drehmomentbegrenzers einen Stapel aus Feder- und Kunststoffscheiben aufweisen. Die Axialarretiervorrichtung kann ferner ein Zentrierstück aufweisen, auf dem die Hysteresekassette in Bezug auf das Primärschwungrad zentriert ist;
• - In einem weiteren Beispiel kann die Axialarretiervorrichtung zwei Hysteresekassetten aufweisen, die axial auf der einen und auf der anderen Seite des Drehmomentbegrenzers angeordnet sind und vorzugsweise spielfrei am Drehmomentausgangsorgan des Drehmomentbegrenzers anliegen. Die Axialarretiervorrichtung kann ferner ein Zentrierstück aufweisen, auf dem die Hysteresekassette in Bezug auf das Primärschwungrad zentriert ist;

This axial stack of discs can comprise at least one disc of the elastic type, preferably conical;

• - Alternatively or in combination, the axial locking device consist of at least one hysteresis cassette, which is formed from at least one guide cage and a spring washer. The at least one cassette may be interposed between the primary flywheel and the torque output member of the torque limiter. The guide cage can be mounted in axial contact with the torque output member of the torque limiter. The spring washer can be conically shaped at an angle of inclination α1, α2 in relation to the at least one guide cage;
• For example, a hysteresis cassette of the axial locking device can comprise a spring washer interposed between two guide cages which are coaxial and superimposed on centering rims which are in particular arranged axially opposite one another. One of the guide cages can be housed in a material recess of the additional end of the locking component. The two guide cages can be connected to one another by locking means of the snap-in type, which are of complementary design;
• - In another example, a hysteresis cassette of the axial locking device may comprise a spring washer interposed between a single guide cage and a cover of the primary flywheel. In a particular embodiment, this guide cage can be centered by the cover of the primary flywheel via a collar-type centering support. In another particular embodiment, this guide cage can be retained by the cover, preferably by locking means of the snap-in type;
• - In a first example, the axial locking device may comprise a hysteresis cartridge on one axial side of the torque limiter and a stack of discs on the other axial side of the torque limiter. The axial locking device may further include a centering piece on which either the hysteresis cassette or the stack of spring and plastic washers is centered with respect to the primary flywheel;
• In another example, the axial locking device may comprise, on the same axial side of the torque limiter, a centering piece on which a stack of spring and plastic washers is centered;
• In another example, the axial locking device may include a hysteresis cartridge on one axial side of the torque limiter and a stack of spring and plastic washers on the other axial side of the torque limiter. The axial locking device may further comprise a centering piece on which the hysteresis cassette is centered with respect to the primary flywheel;
• In a further example, the axial locking device can have two hysteresis cassettes which are arranged axially on one side and on the other side of the torque limiter and which preferably bear against the torque output element of the torque limiter without play. The axial locking device may further comprise a centering piece on which the hysteresis cassette is centered with respect to the primary flywheel;

1. a) Bereitstellen zumindest von:
   • - einer Mitnehmerscheibe mit einer Rotationsachse X,
   • - einer Dichtungsscheibe,
   • - zwei Sicherungshaltern mit gebogenen Formen und unterschiedlichen Außendurchmessern und
   • - ersten Befestigungsmitteln, z.B. eine Reihe von Nieten;
2. b) Herstellen eines zusätzlichen Endes, das für die axiale Arretierung eines Rollorgans ausgebildet ist durch Materialverformung und/oder Entfernen von Material von einer Arretierkomponente ausgewählt aus den Sicherungshaltern, der Dichtungsscheibe und den ersten Befestigungsmitteln;
3. c) Aufnahme der Mitnehmerscheibe zwischen den beiden Sicherungshaltern;
4. d) Einklemmen der Mitnehmerscheibe zwischen den beiden Sicherungshaltern, und dann festes Verbinden der Sicherungshalter mit der Dichtungsscheibe, so dass die Mitnehmerscheibe zwischen den beiden Sicherungshaltern eng angebracht ist.

According to a fourth aspect, the subject matter of the invention is also a method for producing a torque limiter for a damping device, which comprises at least the following steps:

1. a) Providing at least:
   • - a drive plate with an axis of rotation X,
   • - a sealing washer,
   • - two fuse holders with curved shapes and different outside diameters and
   • - first fastening means, for example a series of rivets;
2. b) producing an additional end adapted for the axial locking of a rolling element by material deformation and/or material removal from a locking component selected from the fuse holders, the sealing washer and the first fastening means;
3. c) receiving the drive plate between the two fuse holders;
4. d) Clamping the drive plate between the two fuse holders, and then firmly connecting the fuse holder ter with the sealing washer so that the drive washer is tightly fitted between the two fuse holders.

This process produces a pre-assembled torque limiter, here a unitary assembly that performs multiple functions including torque transmission, sealing, and axial retention of a rolling member. The axial locking of such a component of the limiter is easy to implement. Starting from its end, a simple step b) of material deformation and/or material removal is carried out to form the additional end.

This additional end, which has a special shape, is designed to ensure a more stable and reliable grip of the rolling body.

Assembly steps c) and d) ensure that the drive plate can be sandwiched and thereby slide between two fuse holders, regardless of the attachment of these fuse holders. The fuse holders become the elements contributing to the axial loading of the torque limiter. This limits the risk of component breakage under excessive torque conditions. Your lifespan will be increased.

This manufacturing process can adopt all or some of the features previously mentioned.

• - Die Sicherungshalter können Reibbeläge aufweisen, die vor dem Zusammenbau geschmiert, z. B. vorher in einem Ölbad getaucht werden. Durch Schritt d) wird das gesamte Öl, das nicht von den Belägen absorbiert wird, während des Montagevorgangs ausgetrieben. Dadurch wird die Schmierung der Beläge und des Begrenzers optimiert;
• - Gemäß Schritt b) kann das zusätzliche Ende der Arretierkomponente hergestellt werden:
• - durch Tiefziehen oder Biegen der Arretierkomponente zur Bildung eines Kragens und/oder
• - durch maschinelle Bearbeitung der Arretierkomponente zur Bildung eines Hohlraums;
• - Gemäß Schritt b) kann die Materialverformung und/oder das Entfernen von Material im Inneren der ausgewählten Arretierkomponente erfolgen. Mit anderen Worten ist das zusätzliche Ende ein radial inneres Ende;
• - Das zusätzliche Ende kann zur Bildung eines Kragens z.B. durch Tiefziehen oder Biegen der Dichtungsscheibe an der Dichtungsscheibe hergestellt werden;
• - Das zusätzliche Ende kann z.B. an einem der Sicherungshalter hergestellt werden:
• - durch Tiefziehen oder Biegen des Sicherungshalters zur Bildung eines Kragens und/oder
• - durch maschinelle Bearbeitung des Sicherungshalters zur Bildung eines Hohlraums;
• - Als Beispiel kann das zusätzliche Ende zumindest an einigen der Befestigungsmittel hergestellt werden:
• - durch Tiefziehen oder Materialverlängerung zur Bildung eines Vorsprungs oder Nietkopfes und/oder
• - durch maschinelle Bearbeitung der Befestigungsmittel zur Bildung eines Hohlraums;
• - Die bogenförmigen Sicherungshalter können einen Freiraum begrenzen, in dem die Mitnehmerscheibe teilweise untergebracht ist;

Gegenstand der Erfindung ist gemäß einem fünften Aspekt auch ein Montagesatz für ein Fahrzeuggetriebe mit einem vormontierten Drehmomentbegrenzer, der alle oder einen Teil der oben genannten Merkmale übernehmen kann.This manufacturing process according to the invention can have one or the other of the features described below, which can be combined with one another or used independently of one another:

• - The fuse holders may have friction linings that need to be lubricated before assembly, e.g. B. previously immersed in an oil bath. Step d) expels all oil not absorbed by the pads during the assembly process. This optimizes the lubrication of the pads and the limiter;
• - According to step b) the additional end of the locking component can be made:
• - by deep-drawing or bending the locking component to form a collar and/or
• - by machining the locking component to form a cavity;
• - According to step b), the material deformation and/or the removal of material can take place inside the selected locking component. In other words, the additional end is a radially inner end;
• - The additional end can be made to form a collar, for example by stamping or bending the washer on the washer;
• - The extra end can be made e.g. on one of the fuse holders:
• - by deep drawing or bending the fuse holder to form a collar and/or
• - by machining the fuse holder to form a cavity;
• - As an example, the extra end can be made at least on some of the fasteners:
• - by deep drawing or lengthening of material to form a projection or rivet head and/or
• - by machining the fasteners to form a cavity;
• - The arcuate fuse holders can delimit a space in which the drive plate is partially housed;

According to a fifth aspect, the subject matter of the invention is also an assembly kit for a vehicle transmission with a preassembled torque limiter, which can adopt all or part of the features mentioned above.

• - ein Rollorgan oder eine Axialarretiervorrichtung, ein Primärschwungrad und ein Sekundärschwungrad; und/oder
• - eine Torsionsdämpferbaugruppe, die z. B. Federn aufweist; und/oder
• - einen Kupplungsmechanismus; und/oder
• - eine Drehmomentübertragungswelle, bei der es sich um eine drehbar mit einem Motor gekoppelte Antriebswelle handeln kann; und/oder
• - ein Kupplungsausrücklager;

According to this aspect of the invention, the kit may further include:

• - a rolling element or an axial locking device, a primary flywheel and a secondary flywheel; and or
• - a torsional damper assembly, e.g. B. has springs; and or
• - a clutch mechanism; and or
• - a torque transfer shaft, which may be a drive shaft rotatably coupled to a motor; and or
• - a clutch release bearing;

According to a sixth aspect, the subject matter of the invention is also an assembly kit for a vehicle transmission with a damping device, which can adopt all or part of the aforementioned features.

• - einen Kupplungsmechanismus; und/oder
• - eine Drehmomentübertragungswelle, bei der es sich um eine drehbar mit einem Motor gekoppelte Antriebswelle handeln kann; und/oder
• - ein Kupplungsausrücklager;

According to these aspects of the invention, the kit may further include:

• - a clutch mechanism; and or
• - a torque transfer shaft, which may be a drive shaft rotatably coupled to a motor; and or
• - a clutch release bearing;

• - 1 ist eine perspektivische Ansicht einer Dämpfungsvorrichtung mit einem Drehmomentbegrenzer gemäß einer ersten Ausführungsform der Erfindung;
• - 2 ist ein Axialschnitt der Dämpfungsvorrichtung gemäß der in 1 gezeigten ersten Ausführungsform;
• - 3 ist eine Detailansicht des Drehmomentbegrenzers gemäß der in 1 gezeigten ersten Ausführungsform;
• - 4 ist eine perspektivische Ansicht des Drehmomentbegrenzers gemäß der in 1 gezeigten ersten Ausführungsform;
• - 5 ist eine perspektivische Detailansicht des Drehmomentbegrenzers gemäß der in 1 gezeigten ersten Ausführungsform;
• - 6, 7 und 8 beschreiben ein Verfahren zur Herstellung des Drehmomentbegrenzers gemäß der ersten Ausführungsform;
• - 9 ist eine perspektivische Ansicht des Drehmomentbegrenzers gemäß einer zweiten Ausführungsform der Erfindung;
• - 10 ist eine Vorderansicht des Drehmomentbegrenzers gemäß der in 9 gezeigten zweiten Ausführungsform;
• - 11 ist ein Axialschnitt des Drehmomentbegrenzers gemäß der in 9 gezeigten zweiten Ausführungsform;
• - 12 ist ein Axialschnitt des Drehmomentbegrenzers gemäß einer dritten Ausführungsform der Erfindung;
• - 13 ist ein Axialschnitt des Drehmomentbegrenzers gemäß einer vierten Ausführungsform der Erfindung;
• - 14 ist ein Axialschnitt des Drehmomentbegrenzers gemäß einer fünften Ausführungsform der Erfindung;
• - 15 ist eine Variante des Drehmomentbegrenzers gemäß der in 14 gezeigten fünften Ausführungsform im Axialschnitt;
• - 16 ist ein Axialschnitt des Drehmomentbegrenzers gemäß einer sechsten Ausführungsform der Erfindung;
• - 17, 18 und 19 sind Varianten einer Dämpfungsvorrichtung gemäß einer siebten Ausführungsform der Erfindung im Axialschnitt;
• - 20, 21 sind Varianten einer Dämpfungsvorrichtung gemäß einer achten Ausführungsform der Erfindung im Axialschnitt;
• - 22 ist ein Axialschnitt der Dämpfungsvorrichtung gemäß einer neunten Ausführungsform der Erfindung;
• - 23 ist eine Explosionsansicht einer ersten Hysteresekassette gemäß der neunten Ausführungsform von 22;
• - 24 ist ein Axialschnitt der ersten Hysteresekassette gemäß der neunte Ausführungsform von 22;
• - 25 ist ein Axialschnitt der zweiten Hysteresekassette gemäß der neunte Ausführungsform von 20;
• - 26 ist eine Variante der zweiten Hysteresekassette der neunten Ausführungsform im Axialschnitt;
• - 27 ist ein Axialschnitt der Dämpfungsvorrichtung gemäß einer zehnten Ausführungsform der Erfindung;

The invention will be better understood and other aims, details, characteristics and advantages will become more apparent during the course of the following description of a particular embodiment of the invention, given purely by way of illustration and not of limitation, and with reference to the attached figures:

• - 1 12 is a perspective view of a damper device with a torque limiter according to a first embodiment of the invention;
• - 2 is an axial section of the damping device according to FIG 1 shown first embodiment;
• - 3 is a detailed view of the torque limiter according to FIG 1 shown first embodiment;
• - 4 12 is a perspective view of the torque limiter according to FIG 1 shown first embodiment;
• - 5 is a detailed perspective view of the torque limiter according to FIG 1 shown first embodiment;
• - 6 , 7 and 8th describe a method of manufacturing the torque limiter according to the first embodiment;
• - 9 12 is a perspective view of the torque limiter according to a second embodiment of the invention;
• - 10 is a front view of the torque limiter according to FIG 9 second embodiment shown;
• - 11 is an axial section of the torque limiter according to the in 9 second embodiment shown;
• - 12 13 is an axial section of the torque limiter according to a third embodiment of the invention;
• - 13 Fig. 12 is an axial section of the torque limiter according to a fourth embodiment of the invention;
• - 14 13 is an axial section of the torque limiter according to a fifth embodiment of the invention;
• - 15 is a variant of the torque limiter according to in 14 shown fifth embodiment in axial section;
• - 16 12 is an axial section of the torque limiter according to a sixth embodiment of the invention;
• - 17 , 18 and 19 are variants of a damping device according to a seventh embodiment of the invention in axial section;
• - 20 , 21 are variants of a damping device according to an eighth embodiment of the invention in axial section;
• - 22 Fig. 12 is an axial section of the damping device according to a ninth embodiment of the invention;
• - 23 FIG. 14 is an exploded view of a first hysteresis cartridge according to the ninth embodiment of FIG 22 ;
• - 24 13 is an axial section of the first hysteresis cassette according to the ninth embodiment of FIG 22 ;
• - 25 13 is an axial section of the second hysteresis cassette according to the ninth embodiment of FIG 20 ;
• - 26 13 is a variant of the second hysteresis cassette of the ninth embodiment in axial section;
• - 27 Fig. 12 is an axial section of the damping device according to a tenth embodiment of the invention;

"Mobility machine" means motor vehicles, including passenger cars, but also industrial vehicles, in particular trucks, public transport or agricultural vehicles, as well as any transport machine capable of moving a living being and/or an object from one point to another . It may include a hybrid drive, an electric drive, and/or a low mobility drive.

Unless otherwise specified, “axial” means “parallel to the axis of rotation X of the damping device or torque limiter”; "radial" means "along a transverse axis that intersects the axis of rotation of the damping device or torque limiter"; "angularly" or "circumferentially" "about the axis of rotation X of the damping device or torque limiter".

In the remainder of the description and claims, the terms “internal/internal” or “external/external” will be used in relation to the X axis and in a radial orientation orthogonal to the axial orientation and in a non-limiting manner for better understanding the terms "rear" AR and "front" AV for definition the relative position of one element with respect to another in the axial direction, with a member intended to be located close to the engine being referred to as a rear member and an element intended to be placed close to the transmission being referred to as a front member referred to as. The thicknesses EP1, EP2, EP3 are measured here along the X axis of rotation.

Certain elements, such as the first or second fasteners or the primary flywheel or secondary flywheel, may be indexed in the description. This is a simple indexing to distinguish and name items that are similar but not identical. This indexing does not imply a priority of one element over another, and such designations can be easily interchanged without departing from the scope of the present description.

• - ein Primärschwungrad 2, das zur Befestigung an einer Antriebswelle wie der Kurbelwelle eines Verbrennungsmotors vorgesehen ist, und
• - ein Sekundärschwungrad 3, das auf das Primärschwungrad 2 zentriert und mit einem Rollorgan, Lager 6 genannt, z.B. ein Zentrierlager für das Sekundärschwungrad 3 darauf geführt ist, und
• - einen Torsionsdämpfer 4, der mindestens eine Reihe von elastischen Organen 40 umfasst, die es ermöglichen, das Drehmoment zu übertragen und die Drehungleichförmigkeiten zwischen dem Primärschwungrad 2 und dem Sekundärschwungrad 3 zu dämpfen, um die vom Motor des Kraftfahrzeugs stammenden Vibrationen zu reduzieren;
• - einen Drehmomentbegrenzer 5, der Folgendes aufweist:
• - ein Eingangsorgan 5A, das aus einer Mitnehmerscheibe 51 gebildet ist, die mit den elastischen Organen 40 zusammenwirkt;
• - ein mehrteiliges Ausgangsorgan 5B, das mit dem Eingangsorgan 5A zusammenwirkt und fest am Sekundärschwungrad 3 befestigt ist.

It will be on the 1 until 2 Reference is made to FIG. 1, which show a damping device 1 of a drive chain, such as a dual-mass flywheel, according to a first embodiment. The dual-mass flywheel also has the following:

• - a primary flywheel 2 intended to be fixed to a drive shaft such as the crankshaft of an internal combustion engine, and
• - a secondary flywheel 3 centered on the primary flywheel 2 and guided thereon with a rolling member called bearing 6, eg a centering bearing for the secondary flywheel 3, and
• a torsional damper 4 comprising at least one series of elastic members 40 allowing torque transmission and dampening the torsional irregularities between the primary flywheel 2 and the secondary flywheel 3 in order to reduce the vibrations coming from the motor vehicle engine;
• - a torque limiter 5 comprising:
• an input member 5A made up of a drive washer 51 cooperating with the elastic members 40;
• a multipart output member 5B cooperating with the input member 5A and fixed to the secondary flywheel 3.

The input device 5A and the output device 5B of the torque limiter 5 are in 5 shown partially torn off. The input member 5A and the output member 5B are superimposed radially along the X axis and are, for example, partially contained in a plane P perpendicular to the X axis.

By "drive washer" 51 is meant an elastic or flexible washer, for example of the Belleville type, which is rotationally symmetrical, has the axis X and is circumferentially continuous over 360 degrees. In addition, the drive plate 51 can axially define the center of the torque limiter. The drive disc must be perpendicular to the X axis and is penetrated in particular by the P plane. This plane P can define a plane of symmetry for the assembly of identical or double components of the torque limiter, in particular for the multi-part output member 5B.

Moreover, the flex plate 51 radially extends between an inner diameter DE1 and an outer diameter DE2 in a planar linear shape. The drive plate can be distinguished from an intermediate cover in that the drive plate has an inner diameter DE1 much larger than that of a simple cover.

In addition, the drive plate is formed over its entire surface, i.e. free of windows and grooves.

Moreover, the primary flywheel 2 and the secondary flywheel 3 are designed to be mounted movably about a rotation axis X, and are also rotatable about the axis X with respect to each other.

• - eine radial innere primäre mittlere Nabe 25, die das Lager 6 mit dem Sekundärschwungrad 3 trägt,
• - einen sich radial erstreckenden ringförmigen Abschnitt 22, der als primäre Masse bezeichnet wird, und
• - einen zylindrischen Abschnitt 23, der sich auf der zum Motor entgegengesetzten Seite ausgehend von dem Außenumfang des ringförmigen Abschnitts 22 axial erstreckt. Das Primärschwungrad 2 weist auch einen ringförmigen Deckel 24 auf, der am zylindrischen Abschnitt 23 befestigt ist. Der ringförmige Deckel 24 definiert mit dem ringförmigen Abschnitt 22 und dem zylindrischen Abschnitt 23 eine ringförmige Kammer 28.

The primary flywheel 2 also includes:

• - a radially inner primary central hub 25 carrying the bearing 6 with the secondary flywheel 3,
• - a radially extending annular portion 22, referred to as the primary mass, and
• a cylindrical portion 23 extending axially from the outer periphery of the annular portion 22 on the opposite side to the motor. The primary flywheel 2 also has an annular cover 24 fixed to the cylindrical portion 23 . The annular cover 24 defines an annular chamber 28 with the annular portion 22 and the cylindrical portion 23.

In addition, the cover 24 is firmly attached to the cylindrical portion 23, in particular by welding 100. FIG.

In addition, the primary flywheel 2 carries on its outer circumference a ring gear 26 for driving the primary flywheel 2 in rotation with the aid of a starter. In 2 For example, openings 259 are formed in center hub 25 opposite openings 229 formed in the radially inner portion of annular portion 22 of the primary flywheel. Mounting bolts, not shown, engaging these openings allow the primary flywheel to be secured to the end of the driveshaft. Likewise, the secondary flywheel 3 may have openings (not shown) intended for the passage of bolts when assembling the dual-mass flywheel on the drive shaft.

In operation, the elastic members 40 are pressed outwards against the cylindrical portion 23 by the centrifugal force acting thereon. Therefore, in the annular chamber 28, between the cylindrical portion 23 of the primary flywheel 2 and the outer periphery of the elastic members 40, guiding members in the form of grooves 41 are mounted. The channels 41 are formed from a longitudinally and transversely bent metal sheet.

In order to limit the friction between the elastic members 40 and the cylindrical portion 23 of the primary flywheel 2, the annular chamber 9 is filled with a lubricant, preferably grease or oil.

In order to prevent lubricant from escaping from the annular chamber 24 to the outside, the torque limiter 5 also has at least one disc 58 which ensures the tightness of the primary and secondary flywheel.

In the examples shown, a single washer 58 extends radially between the cover 24 and the secondary hub 35. This washer 58 also extends radially between an inner diameter DF1 and an outer diameter DF2 in a stepped configuration.

• - einen ersten Abschnitt, der am Deckel 24 anliegt; und
• - einen zweiten Abschnitt, der zwischen dem Ausgangsorgan 5B und der sekundären Nabe 35 axial anliegend eingefügt ist.

In the first embodiment, the sealing disk 58 further comprises first and second sealing sections which are axially offset from one another.

• - a first portion which bears against the cover 24; and
• a second portion interposed between the output member 5B and the secondary hub 35 in an axially abutting manner.

In addition, the sealing disk 58 is axially sandwiched between the fuse holder 53 and the secondary hub 35 and in particular is inserted between them and fixedly attached thereto, in particular by means of a rivet connection.

• - einerseits mit dem Ausgangsorgan 5B des Drehmomentbegrenzers über erste Befestigungsmittel 71; und
• - andererseits mit dem Sekundärschwungrad 3 über zweite Befestigungsmittel 72.

In particular, the washer 58 is firmly attached:

• on the one hand to the output member 5B of the torque limiter via first attachment means 71; and
• - on the other hand with the secondary flywheel 3 via second fastening means 72.

In addition, the primary flywheel has mounting through holes 27 in the annular portion 22 for handling and attachment of the fasteners 72 . For this purpose, these through-openings 27 are designed as openings in the fastening means 72 and, after they have been joined together, are closed with sealing plugs 57 for an optional closure, which are pressed into the through-openings 27 .

In an embodiment not shown, the torque limiter may comprise a plurality of discs 58, 59, for example two sealing discs 58, arranged axially on one side of the cover 24 and on the other.

In addition, the elastic members 40 are curved with circumferential action, such as helical springs housed in the annular chamber 28 and distributed circumferentially about the X axis. The drive washer 51 has fingers 514, here two, which cooperate with the elastic members 40 in the circumferential direction.

In addition, each curved elastic member 40 can comprise two coaxial springs fitted one inside the other.

• - einerseits zwischen zwei Stützsitzen 220, die am Primärschwungrad 2 ausgebildet sind, und
• - andererseits zwischen zwei Stützlaschen 514, die an der Mitnehmerscheibe 51 des Drehmomentbegrenzers ausgebildet sind.

In addition, the elastic organs 40 extend:

• - on the one hand between two support seats 220 formed on the primary flywheel 2, and
• - on the other hand, between two support tabs 514 formed on the drive plate 51 of the torque limiter.

Also, each support seat 230 carried by the primary flywheel 2 consists of a boss formed in the annular portion 22 and a boss formed in the cover 24. As shown in FIG.

In operation, the elastic members 40 bear with a first end on a bearing seat 220 carried by the primary flywheel 2 and with a second end on a driver mer disc 51 trained support bracket 514 from to ensure the transmission of torque between the primary flywheel 2 and the torque limiter 5.

In this way, the torque from the crankshaft is transmitted to the primary flywheel 2, which compresses the elastic members 40. These are supported on the tabs 514 and drive the compressed drive disk 51, which interacts with the fuse holders 52, 53 by friction. These fuse holders 52, 53 in turn drive the secondary flywheel 3.

• - eine radial innere sekundäre Nabe 35 oder einen radial inneren sekundären Flansch, die bzw. der das Lager 6 zentriert,
• - einen ringförmigen Abschnitt 32, Sekundärmasse genannt, der sich radial erstreckt, und
• - einen zylindrischen Abschnitt, der als Außenrand 33 bezeichnet wird und sich auf der zum Motor entgegengesetzten Seite ausgehend von dem Außenumfang des ringförmigen Abschnitts 32 axial erstreckt.

In addition, the secondary flywheel 3 has the following:

• - a radially inner secondary hub 35 or a radially inner secondary flange which centers the bearing 6,
• an annular portion 32, called the secondary mass, which extends radially, and
• a cylindrical portion, referred to as the outer edge 33, which extends axially from the outer periphery of the annular portion 32 on the opposite side to the motor.

In the illustrated examples, the cover 24 is radially opposite the secondary hub 35.

• - einen Deckel, der am Außenumfang des Sekundärschwungrads befestigt ist, mindestens eine Kupplungsscheibe, die mit Reibbelägen und einer mit der Antriebswelle verbundenen Keilnabe ausgestattet ist,
• - eine Druckplatte und eine ringförmige Membran, die die Druckplatte axial zum Sekundärschwungrad beaufschlagt. Die Druckplatte kann durch tangentiale, axial wirkende, elastische Zungen, die eine axiale Bewegung der Druckplatte in Bezug auf die Reaktionsplatte zulassen, drehbar mit dem Deckel verbunden sein; und
• - ein Kupplungsausrücklager, das die Membrane 17 verschwenken kann, so dass die Kupplung in ihre ausgerückte Position bewegt wird.

In addition, the secondary flywheel 3 is intended to form the reaction plate of a clutch, not shown. The dual mass flywheel may therefore include a clutch mechanism that also includes:

• - a cover fixed to the outer periphery of the secondary flywheel, at least one clutch disc equipped with friction linings and a splined hub connected to the drive shaft,
• - a pressure plate and an annular diaphragm that acts on the pressure plate axially to the secondary flywheel. The pressure plate may be pivotally connected to the cover by tangential axially acting resilient tongues allowing axial movement of the pressure plate with respect to the reaction plate; and
• - a clutch release bearing which can pivot the diaphragm 17 so that the clutch is moved to its disengaged position.

In the examples illustrated, the secondary flywheel 3 has openings 330 near its outer edge 33 for fitting the cover 15 of the clutch mechanism by means of studs 22 .

• - durch einen ringförmigen Materialwulst 250 des Primärschwungrads 2 einerseits, der zur Abstützung des Innenrings 61 des Lagers 6 dient und die Endfläche des Innenrings in Richtung des Motors hält;
• - durch eine Stützscheibe 7 andererseits, die zur Abstützung des Innenrings 61 des Lagers 6 dient und die Endfläche des Außenrings in der zum Motor entgegengesetzten Richtung hält;

In addition, the support and the axial retention of the inner ring 61 of the bearing 6 are direct:

• by an annular bead of material 250 of the primary flywheel 2, on the one hand, serving to support the inner ring 61 of the bearing 6 and holding the end face of the inner ring towards the engine;
• by a support washer 7 on the other hand serving to support the inner ring 61 of the bearing 6 and holding the end face of the outer ring in the opposite direction to the motor;

Such a material bead 250 is formed on the outer circumference of the middle hub 25 of the primary flywheel 2 . This material bead 250 can be a collar, a flange, a collar or a base, for example. Thus, the inner diameter DR1 of the bearing 6 is firmly attached between the primary flywheel 2 and the support washer 7.

• - durch eine Schulter 350 des Sekundärschwungrads 3 einerseits, die zur Abstützung des Außenrings 62 des Lagers 6 und zum Halten des Außendurchmessers DR2 des Außenrings in der zum Motor entgegengesetzten Richtung dient;
• - durch eine Axialarretierkomponente 9 des Drehmomentbegrenzers 5 andererseits, die zur Abstützung des Außenrings 62 des Lagers 6 dient und den Außendurchmesser DR2 des Außenrings in Richtung des Motors hält;

In addition, the support and the axial retention of the outer ring 62 of the bearing 6 are direct:

• by a shoulder 350 of the secondary flywheel 3, on the one hand, serving to support the outer ring 62 of the bearing 6 and to hold the outside diameter DR2 of the outer ring in the opposite direction to the engine;
• by an axial locking component 9 of the torque limiter 5, on the other hand, serving to support the outer ring 62 of the bearing 6 and keeping the outside diameter DR2 of the outer ring towards the motor;

Such a shoulder 350 is formed on the inner periphery of the hub 35 of the secondary flywheel 3 . Thus, the outer diameter DR2 of the bearing 6 is fixed between the secondary flywheel 3 and the torque limiter 5.

In particular, the torque output member 5B and the bearing 6 are arranged radially one above the other. In a variant that is not shown, the rolling element can be replaced by a plain bearing.

The component 9 for locking the bearing is significant in that it is selected from the components of the torque limiter 5 except for the torque input member 5A of the torque limiter.

In addition, the locking component 9 is significant in that it has an additional end 90 has been previously modified to better support the bearing.

Such an additional end 90 is formed by material deformation and/or material removal. In the illustrated examples, the additional end 90 is a modified radially inner end of the locking component 9.

In addition, this additional end 90, together with the adjacent components of the torque limiter 5, delimits an internal housing 93 in which the bearing 6 is at least partially housed.

Various embodiments of such a locking component 9 of the torque limiter are described below.

• - zwei rotationssymmetrischen Sicherungshaltern 52, 53 mit der Achse X; und
• - ersten Befestigungsmitteln 71 zur festen Verbindung der Sicherungshalter 52, 53;

The multi-part starting element 5B (which can also be referred to as the phase element) preferably consists of:

• - Two rotationally symmetrical fuse holders 52, 53 with the axis X; and
• - first fastening means 71 for the fixed connection of the fuse holders 52, 53;

The fuse holders 52, 53 can essentially have the same structure as in FIGS 11 until 16 you can see. Preferably, the holders 52, 53 are flared plates or discs of the cup type with radially outer end portions which externally receive the drive disc.

In addition, these holders 52, 53 are arranged axially in series. In particular, they are arranged axially on one side and on the other side of the plane P, and their curved shapes can be symmetrical about the plane P.

In addition, the fuse holders 52, 53 are produced by cold forming, in particular by deep drawing, of the material of the radially inner circumference. These holders 52, 53 are made of steel, produced here by hardening.

As a variant, they can be made by bending or by any other means of cold working.

In addition, these fuse holders 52, 53 may be disk-shaped laminations with solid shapes that are circumferentially continuous over 360 degrees, i.e., devoid of windows to accommodate springs.

• - Einer der Halter 52 hat eine kleinere radiale Ausdehnung mit einem kleinen Außendurchmesser DS2. Somit erstreckt sich der sogenannte untere Halter 52 radial zwischen einem Innendurchmesser DS1 und einem Außendurchmesser DS2;
• - Der andere Halter 53 hast eine größere radiale Ausdehnung mit einem großen Außendurchmesser DS2. Somit erstreckt sich der sogenannte obere Halter 53 radial zwischen einem Innendurchmesser DS1' und einem Außendurchmesser DS2';
• - Die Dicke Ep2 des Halters 52 kann kleiner oder als Variante größer sein als die Dicke Ep3 des Halters 53;

In addition, it is possible to differentiate between the two fuse holders 52, 53 by their different dimensions, in particular by their inner diameter, their outer diameter and their radial extent:

• - One of the holders 52 has a smaller radial extension with a small outer diameter DS2. Thus, the so-called lower holder 52 extends radially between an inner diameter DS1 and an outer diameter DS2;
• - The other holder 53 has a greater radial extent with a large outer diameter DS2. Thus, the so-called upper holder 53 extends radially between an inner diameter DS1' and an outer diameter DS2';
• the thickness Ep2 of the support 52 can be less or, as a variant, greater than the thickness Ep3 of the support 53;

As shown in the examples, the outer diameter DS2 of the holder 52 (called the lower holder) is smaller than the outer diameter DS2' of the holder 53 (called the upper holder). In addition, the so-called lower fuse holder 52 can be arranged on the engine side, i.e. axially farthest from the secondary flywheel 3. The so-called upper fuse holder 53 can be located on the transmission side, i.e. axially closest to the secondary flywheel 3.

The inside diameter DE1 of the drive disk 51 is e.g. 1.3 times larger than the inside diameters DS1, DS1' of the fuse holders 52 and 53.

For each fuse holder 52, 53, its thickness Ep2, Ep3 is substantially the same over the entire length of the part. The thicknesses Ep1, Ep2 of the fuse holders 52, 53 are, for example, between 0.5 and 2 mm, preferably of the order of 0.8 mm. Thus, despite the small thickness of the fuse holders 52, 53, the torque output member 5B still offers large support surfaces for the elastic members 40.

In a variant that is not shown, the thicknesses of the fuse holders can be identical.

In a further variant, not shown, the fuse holders can be shaped identically in order to further simplify the production of the torque output element.

• - Mittelstege 525, 535, wobei diese axial aufliegen und so ausgebildet sind, dass sie mit ersten Befestigungsmitteln 71, insbesondere über eine Nietverbindung oder durch Abstandshalter, aneinander befestigt sein können;
• - ein radiales ringförmiges Endstück oder eine radiale ringförmige Flanke 520, 530, wobei diese axial gegenüberliegen und so ausgebildet sind, dass sie den Freiraum C0 begrenzen, der die Mitnehmerscheibe 51 aufnimmt.

As illustrated in the examples, each fuse holder 52, 53 also includes:

• - Central webs 525, 535, which rest axially and are designed so that they with first fasteners 71, in particular via a rivet connection or by spacers, may be attached to each other;
• a radial annular end piece or flank 520, 530, these being axially opposed and shaped so as to delimit the free space C0 accommodating the drive washer 51.

In addition, the inner diameter DE1 is defined by the bore of the driver disk 51, which is referred to as the central window 516, in which the holders 52, 53, in particular their central webs 525, 535, are partially fitted.

Each center bar 525, 535 defines the inner diameter DS1, DS1' of the corresponding fuse holder.

The inside diameters DS1, DS1' of the fuse holders can have identical or different dimensions.

In addition, each flank 520, 530 defines the outer diameter DS2, DS2' of the corresponding fuse holder.

In addition, the inside diameter DS1 is defined by the bore of the fuse holder 52, referred to as the center window 526, in which the bearing 6 is partially mounted. In addition, the inner diameter DS1' is defined by the bore of the other fuse holder 53, referred to as the central window 536, in which the bearing 6 is partially mounted.

In addition, the receptacle 93 is delimited radially by the fuse holders 52, 53 and the sealing washer 58. The receptacle 93 is limited in particular radially by the central windows 526, 536 of the holders 52, 53.

As an example, the plane P contains the center windows 516, 526. Here, the center windows 526, 536 of the holders are radially aligned with the center window 516 of the drive plate, which limits space requirements.

• - koaxiale Öffnungen 521, 531 für den Durchgang von ersten Befestigungsmitteln 71, hier achtzehn an der Zahl; und
• - koaxiale Öffnungen 522, 532 für den Durchgang von zweiten Befestigungsmitteln 72, hier neun an der Zahl.

In addition, each center bar 525, 535 further includes:

• coaxial openings 521, 531 for the passage of first fastening means 71, here eighteen in number; and
• coaxial openings 522, 532 for the passage of second fastening means 72, here nine in number.

• - Löcher 581, hier achtzehn an der Zahl, die koaxial zu den Öffnungen 521, 531 für die ersten Befestigungsmittel 71 sind; und
• - Löcher 582, hier neun an der Zahl, die koaxial zu den Öffnungen 522, 532 für die zweiten Befestigungsmittel 72 sind.

In an analogous manner, the sealing disk 58 also has the following:

• holes 581, here eighteen in number, coaxial with the openings 521, 531 for the first fastening means 71; and
• holes 582, here nine in number, coaxial with the openings 522, 532 for the second fastening means 72.

Therefore, these openings 521, 531, 581 and 522, 532, 582 are here bores of the parts, at least some of which can be formed in pairs symmetrically to the axis of each opening.

Furthermore, the first fastening means 71, here rivets, can be defined by a circle C1 for locating the openings 521, 531, 581 that receive the rivets, here defined on the central webs 525, 535. Thus, the openings 521, 531 and the holes 581 are identical in shape, have the same area, here continuous, are aligned on the same arrangement circle C1 and are coaxial with the axes R1. The R1 mounting axes are parallel to the X axis.

Furthermore, the second fastening means 72, here rivets, can be defined by a circle C2 for locating the openings 522,532,582 receiving the rivets, which is also defined on the central webs 525,535. Thus, the orifices 521, 531 and the holes 581 are identical in shape, have the same area, here continuous, are aligned on the same array circle C2 and are coaxial with the axes R2. The R2 mounting axes are parallel to the X axis.

In the illustrated examples, the locating circles C1, C2 have different diameters.

In particular, the arrangement circle C1 encloses the arrangement circle C2.

As a result, the first fastening means 71 enable the drive plate to be assembled with the fuse holders during the pre-assembly of the components of the torque limiter 5. The first fastening means 71 are for assembling the fuse holder and the sealing washer inside the torque limiter.

In addition, the second fasteners 72 allow the preassembled torque limiter to be attached to the secondary flywheel 3. In other words, all the fuse holders and the drive plate are assembled with the secondary flywheel 3. Therefore, the secondary hub 35 may have a mounting interface that receives the second fastener 72, also shown in aperture gene 352 that pass through the axes R2.

• - einen Schaft 710, der die Öffnungen 521, 531, 581 der Halter 52, 53 und der Dichtungsscheibe 58 durchquert; und
• - zwei Köpfe 711, die auf der Motorseite und der Getriebeseite angeordnet sind und jeweils axial anliegend am mittleren Steg 525 des Halters 52 und axial anliegend an der Dichtungsscheibe 58 ausmünden.

As illustrated in the examples, each rivet (which partially forms the first fasteners 71) has:

• a shank 710 passing through the openings 521, 531, 581 of the supports 52, 53 and of the sealing washer 58; and
• two heads 711, located on the engine side and on the transmission side, which open out axially against the central web 525 of the support 52 and axially against the sealing washer 58, respectively.

• - einen Schaft 720, der die Öffnungen 521, 531, 581 und 352 der Halter 52, 53, der Dichtungsscheibe 58 und der sekundären Nabe 35 durchquert. Insbesondere haben die Schäfte 720 eine größere axiale Abmessung als die Schäfte 710; und
• - zwei Köpfe 721, die auf der Motorseite und der Getriebeseite angeordnet sind und jeweils axial anliegend am mittleren Steg 525 des Halters 52 und axial anliegend an der sekundären Nabe 35 ausmünden.

As illustrated in the examples, each rivet (partially forming the second fasteners 72) has:

• a shank 720 passing through the openings 521, 531, 581 and 352 of the supports 52, 53, the sealing washer 58 and the secondary hub 35. In particular, shanks 720 have a greater axial dimension than shanks 710; and
• two heads 721 placed on the engine side and on the transmission side and opening out axially against the central web 525 of the support 52 and axially against the secondary hub 35, respectively.

In operation, there is a risk that the drive plate 51 will break under excessive torque conditions. In order to counteract this disadvantage, a free space C0 is delimited between the supports 52, 53, referred to as the internal compartment or internal volume, in which the input member 5A, here the drive plate, is housed. The clearance allows the drive plate 51 to slide angularly and/or radially with respect to the brackets 52,53.

For this purpose, the fuse holders 52, 53 are axially spaced from one another, in particular at their end pieces or flanks 520, 530, here with an end axial distance L0. This end axial distance L0 is greater than the thickness Ep1 of the drive washer 51 to ensure sliding and the insertion of friction devices.

In addition, flanks 520, 530 of this type are arranged in such a way that they rub against the driver disk 51 by means of friction areas 52F, 53F, which are arranged axially opposite the driver disk 5.

Such friction areas 52F, 53F have the advantage that they limit the relative rotation between the fuse holders 52, 53 and the drive plate 51 in the event of excessive torque, so that this drive plate 51 is protected.

In addition, the friction areas 52F, 53F of the flanks extend radially from their outer diameter DS2, DS2'. Thus, the radially outer edge of each flank 520, 530 has a friction area. At each friction zone 52F, 53F, the fuse holder 52, 53 can have friction linings, for example in the form of layers or segments, in particular of paper, which otherwise require lubrication.

In other words, the output member 5B has two groups of friction linings for coupling between the drive plate and the two fuse holders 52, 53.

The flanks 520, 530 of the fuse-holders can be flexible, which makes it easier to fit the input and output members 5A, 5B together. These bending areas can be angularly inclined slightly and flattened with the drive plate. This ensures a larger frictional contact area between the parts.

In addition, the angle of inclination of the flanks 520, 530 is designed in such a way that, in the assembled state, they have to be pressed flat on one side and on the other side of the driver disk. As a result, a better contact surface between the friction linings 52F, 53F and the drive plate 51 is achieved, regardless of the tolerances.

In addition, the outer edges of the central webs 525, 535 are provided with support means 524, 534 arranged to serve as an internal radial support for the mounting of the drive plate. Each support means 524, 534 integrally connects the central web 525, 535 to the corresponding flank 520, 530 and together they radially define the bottom of the free space C0. In this way, the inside diameter DE1 of the drive disk 51 comes into radial abutment, here abutting, against the bottom of the free space C0 defined between the fuse holders 52, 53.

To avoid unwanted contact or premature failure, the flexplate fingers 514 must be concentric with the other components. For this purpose, at least one of the support means 524, 524 can be designed to complement the shape of the driver disk 51. To this end, the support means 524 of the fuse holder 52 may be defined by a so-called material stamping shoulder 524A to define the inner diameter DE1 of the flexplate during of the assembly process of the torque limiter 5 to center.

Additionally, this stamping of material 524A is formed by cold forming, here by stamping sections of the locking component, here nine in number, that are angularly spaced. This means that there is a discontinuous material embossing around the X axis. These indentations are evenly distributed around the X axis.

In addition, some material indentations may form a crease perpendicular to the corresponding flank 520 and central web 525, particularly in the direction of the drive plate. In this way, these indentations together form shoulder 524A.

In the first embodiment, the axial locking component 9 is formed by the torque output member 5B. The locking component 9 is formed by the fuse holder 52 that is axially furthest away from the secondary flywheel 3 .

In the first embodiment, material deformation is performed on the radially inner periphery of the fuse holder 52 to form the extra end 90 . In particular, the additional end 90 is made by stamping. Deep drawing allows the extra end 90 to be formed into a curved shape.

The locking component 9 is implemented, for example, by the fuse holder 52 with the smaller outer diameter DS2. As a variant, the locking component can be formed by the fuse holder with the larger inner diameter.

The locking component 9 is formed, for example, by the fuse holder 52 with the smaller inside diameter DS1. As a variant, the locking component can be formed by the fuse holder with the larger inner diameter.

Furthermore, the swaged shape of the accessory end 90 is an indented or bent portion, here in the form of a collar 95. As a result, the accessory end 90 defines an inner and/or outer radius of curvature that can vary depending on the positioning of the bearing and torque limiter. In this first embodiment, the stamped shape of the additional end 90 is obtained here by an axial depression greater than the thickness Ep1.

In addition, the additional end 90 has an axial bearing surface 931 for the bearing 6, which is obtained at least partially by stamping. This bearing 6 thus comes into axial abutment against the torque output member 5B and in particular against the axial bearing surface 931 of the additional end 90.

In this first embodiment, the accessory end 90 extends angularly continuously through 360 degrees about the axis X. The accessory end 90 is formed on the inner diameter DS1 of the fuse holder 52 . As a result, the axial support surface 931 for receiving the bearing 6 about the X axis is continuous.

In addition, the seat 93 partially houses the bearing 6 and the hub 35 of the secondary flywheel.

In addition, the additional end 90 and in particular the axial bearing surface 931 and the centering seat 932 delimit the housing 93 which receives the bearing.

• - ist der Außendurchmesser DS2, DS2' des Ausgangsorgans 5B größer als der Innendurchmesser DE1 des Eingangsorgans 5A. Außerdem kann der Außendurchmesser DE2 des Eingangsorgans 5A größer sein als der Außendurchmesser DS2, DS2' des Ausgangsorgans 5B und insbesondere der Sicherungshalter 52, 53;
• - ist der Außendurchmesser DS2' des Sicherungshalters 53, der dem Sekundärschwungrad axial am nächsten liegt, größer als der Außendurchmesser DS2 des Sicherungshalters 52, der von dem Sekundärschwungrad axial am weitesten entfernt ist;
• - kann der Außendurchmesser DS2, DS2' des Ausgangsorgans 5B größer sein als der Außendurchmesser DF2 der Dichtungsscheibe 58;
• - ist der Innendurchmesser DS1 des axial am weitesten von dem Sekundärschwungrad entfernten Sicherungshalters 52 kleiner als der Innendurchmesser DS1' des axial am nächsten zum Sekundärschwungrad liegenden Sicherungshalters 53;
• - kann der Innendurchmesser DS1' des Sicherungshalters 53, der dem Sekundärschwungrad axial am nächsten liegt, kleiner oder gleich dem Innendurchmesser DF1 der Dichtungsscheibe 58 sein.

To illustrate, as shown in the first embodiment:

• - the outer diameter DS2, DS2' of the outlet member 5B is greater than the inner diameter DE1 of the inlet member 5A. Furthermore, the external diameter DE2 of the input member 5A can be greater than the external diameter DS2, DS2' of the output member 5B and in particular the fuse holders 52, 53;
• - the outer diameter DS2' of the fuse holder 53 axially closest to the secondary flywheel is larger than the outer diameter DS2 of the fuse holder 52 axially furthest from the secondary flywheel;
• the outside diameter DS2, DS2' of the output member 5B can be greater than the outside diameter DF2 of the sealing washer 58;
• the inside diameter DS1 of the fuse holder 52 axially furthest from the secondary flywheel is smaller than the inside diameter DS1' of the fuse holder 53 axially closest to the secondary flywheel;
• - the inside diameter DS1' of the fuse holder 53, which is axially closest to the secondary flywheel, can be less than or equal to the inside diameter DF1 of the sealing washer 58.

• Gemäß einem ersten Schritt wird Folgendes bereitgestellt:
  • - eine Mitnehmerscheibe 51 mit einer Rotationsachse X zur Bildung des Drehmomenteingangsorgans 5A;
  • - eine Dichtungsscheibe 58 und
  • - zwei Sicherungshalter 52, 53 zur Bildung des Drehmomentausgangsorgans 5B und
  • - Befestigungsmittel 71, z.B. eine Reihe von Nieten;

The method of manufacturing the torque limiter 5 such as shown in the first embodiment will now be described. This production includes the following steps, among others:

• According to a first step, the following is provided:
  • - a drive plate 51 with an axis of rotation X, constituting the torque input member 5A;
  • - a sealing washer 58 and
  • - Two fuse holders 52, 53 to form the torque output member 5B and
  • - Fastening means 71, for example a series of rivets;

As previously defined, the fuse holders 52, 53 can in particular have arcuate or stepped shapes or axially offset sections. In addition, the fuse holders 52, 53, referred to as lower and upper fuse holders 52 and 53, here have different outside diameters DS2, DS2'.

In a second step (in 6 shown) the material is deformed and/or material is removed from one of the following components of the torque limiter: one of the fuse holders 52, 53 or the sealing washer 58 or the first fastening means 71. The shape of the additional end 90 is designed for the axial locking of the bearing 6 .

This step is carried out to form the extra end 90 inside the locking component 9, i.e. at a radially inner portion of the locking component.

• - eine Kaltumformung der Arretierkomponente zur Bildung eines radial inneren Flansches 95 und/oder
• - eine maschinelle Bearbeitung zur Bildung eines Hohlraums 930.

According to this step, such an additional end 90 can be made by:

• - Cold forming of the locking component to form a radially inner flange 95 and/or
• - a machining to form a cavity 930.

In this step, the cold working can be deep drawing or bending and is achieved here by indenting the material starting from the inside diameter DS1 so as to create an additional end axially offset from the rest of the part material. This deformation of the additional end 90 takes place axially in a direction opposite to the drive plate 51 .

In this first embodiment, the fuse holder 52 is selected as the locking component. Therefore, one of the fuse holders, here the lower fuse holder 52, i. H. the one with the smallest outer diameter, DC2, deep drawn to define an additional end 90. The additional end 90 is in the form of a collar 95 here. The collar 95 is axially offset from the central web 525 .

In particular, the original thickness of the extra end 90 before deformation or before material removal is equal to the thickness Ep2 of the fuse holder.

In this first embodiment, the extra end 90 has no material removed. Therefore, the final thickness of the extra end 90 after deformation or material removal is equal to the thickness Ep2 of the fuse holder.

As a variant, not shown, the extra end 90 can be ground by removing material, here by machining, to form a cavity (not shown). The cavity partially delimits a housing 93 for the rolling element.

In particular, the cavity can be made on the drive plate side and can open out axially onto the bore of the drive plate 51 and the other fuse holder.

According to a third step (in 7 shown) the fuse-holders 52, 53 are arranged, in particular by keeping them spaced axially in order to delimit a clearance C0 between them. Subsequently, the driver disk 51 is inserted axially between the spaced apart fuse holders 52, 53, in particular in this free space C0.

In particular, the drive disk 51, which is flexible or elastic, is mounted within the fuse holders 52, 53 from the outside, in particular by pivoting on one or the other fuse holder 52, 53.

• - Das innere Ende 512 der Mitnehmerscheibe ist auf dem Sicherungshalter 52 am Außendurchmesser DS1 und insbesondere in Anlage an dessen Reibbereich 52F, hier an dessen Reibbelägen angebracht;
• - Ein Zwischenabschnitt 511 der Mitnehmerscheibe ist an dem anderen Sicherungshalter 53 am Außendurchmesser DS1' und insbesondere in Anlage an dessen Reibbereich 53F, hier an dessen Reibbelägen, angebracht.

Pivoting is to be understood here as attachment by pivoting the drive disk to each of the outer ends of the fuse holders 52, 53, in particular to their outer diameter DS1, DS1':

• the inner end 512 of the drive washer is mounted on the fuse holder 52 on the outer diameter DS1 and in particular in contact with its friction zone 52F, here on its friction linings;
• An intermediate portion 511 of the drive washer is attached to the other fuse holder 53 on the outer diameter DS1' and in particular in contact with its friction zone 53F, here its friction linings.

In particular, during this step, the drive plate 51 comes into radial abutment against the bottom of the free space C0 defined between the fuse-holders 52, 53. In 7 the inner diameter DE1 of the drive plate abuts the support means 524, 524 of the fuse holders.

According to a fourth step (in 8th shown), the fuse holders 52, 53 are joined together from the inside, here at their central webs 525, 535, in order to reduce the available free space C0 between the holders.

According to this step, the drive plate 51 is axially clamped between the fuse holders 52, 53 by axially resting on each of the fuse holders 52, 53 by axial supports, as in FIG 8th shown, is pressed. These axial supports, which are formed on one side and on the other side of the holders 52, 53, define the final axial distance L0.

To maintain such clamping, the fuse holders and washer 58 are then fastened together such that the drive washer is retained within the torque limiter. The drive plate is clamped between the fuse holders at the same time. It has no fastening means 71, 72.

The holders 52, 53 and the sealing washer 58 are fastened together with first fastening means 71, here a series of rivets. As an example, these fastening rivets are distributed angularly symmetrically in pairs about the X axis.

In addition, the insertion of these fasteners 71 takes place axially through the coaxial openings 521, 531, 581 formed in the supports 52, 53 and in the sealing washer 58, respectively.

• - das zusätzliche Ende 90 sich winkelmäßig diskontinuierlich um die Achse X erstreckt;
• - die endgültige Dicke des zusätzlichen Endes 90 kleiner ist als die Dicke der Arretierkomponente 9;
• - das zusätzliche Ende 90 durch Entfernen von Material, durch Ausschneiden von mehreren Arretiersegmenten 91 hergestellt wird;
• - das zusätzliche Ende 90 durch Entfernen von Material, durch maschinelle Bearbeitung eines Hohlraums 930 hergestellt wird;

In the 9 until 11 a second embodiment of the invention is described which is substantially similar to the first embodiment except that:

• - the additional end 90 extends angularly discontinuously around the axis X;
• - the final thickness of the additional end 90 is less than the thickness of the locking component 9;
• - the additional end 90 is made by removing material, by cutting out several locking segments 91;
• - the additional end 90 is made by removing material, by machining a cavity 930;

In this second embodiment, the processes of deforming and removing material of the fuse holder 52 to form the extra end 90 are combined. After the end of the fuse holder 52 is deformed by deep drawing, part of the deep drawn material is then removed so that the final thickness of the additional end 90 is less than the thickness Ep2 of the fuse holder 52.

As an example, this removal of material is about 3/4 of the original thickness Ep2 of the fuse holder 52 to realize the resulting final shape of the extra end 90.

In this embodiment, the axial locking segments 91 form the additional end 90. These locking segments 91 are locking lugs, here nine in number, angularly distributed about the axis X in a regular angular distribution of 40 degrees. In a variant that is not shown, these locking segments can also be locking tabs or locking tabs.

For example, the locking segments 91 can be limited axially by cutting incisions. Thus, the additional end 90 consists of an alternating distribution of locking segments 91 and cuts.

In this embodiment, the cavity 930 results from the machined shape of the additional end 90. The resulting thickness of the additional end 90 is therefore less than that of the locking component 9, here by the thickness Ep2.

The cavity 930 in particular partially delimits the housing 93 which receives the bearing 6 .

In addition, the cavity 930 is delimited by the surface 931 for axial support and a centering surface 932 .

In this embodiment, this cavity 930 is delimited by all of the locking segments 91 here. As a result, the axial bearing surface 931 and the centering pad 932 have discontinuous shapes around the X axis.

• - das zusätzliche Ende 90 ausschließlich durch Entfernen von Material, hier durch maschinelle Bearbeitung eines Hohlraums 930 hergestellt wird;
• - die resultierende Enddicke des zusätzlichen Endes 90 um die Dicke Ep2 geringer ist;
• - das zusätzliche Ende 90 z.B. um die Achse X durchgehend sein kann, so dass eine Schulter oder ein Zentrierkranz definiert wird. Dadurch haben die Fläche 931 zur axialen Abstützung und die Zentrierauflage 932, die den Hohlraum 930 begrenzen, hier um die Achse X durchgehende Formen.

In 12 a third embodiment of the invention is described which is substantially similar to the first embodiment except that:

• - the additional end 90 is made solely by removing material, here by machining a cavity 930;
• - the resulting final thickness of the additional end 90 is less by the thickness Ep2;
• the additional end 90 can be continuous around the axis X, for example, so as to define a shoulder or a centering ring. As a result, the axial bearing surface 931 and the centering seat 932 delimiting the cavity 930 are here continuous in shape about the X axis.

• - die Axialarretierkomponente 9 durch die Dichtungsscheibe 58 gebildet ist;
• - das zusätzliche Ende 90 ausschließlich durch Materialumformung, hier durch Tiefziehen oder Biegen, hergestellt wird;
• - die Dichtungsscheibe 58 teilweise im Inneren des Drehmomentausgangsorgans 5B untergebracht ist.

In 13 a fourth embodiment of the invention is described which is substantially similar to the first embodiment except that:

• - the axial locking component 9 is formed by the sealing washer 58;
• - The additional end 90 is produced exclusively by material deformation, here by deep-drawing or bending;
• the sealing washer 58 is partially housed inside the torque output member 5B.

In this fourth embodiment, the inside diameter DF1 of the sealing washer 58 is smaller than the inside diameter DS1, DS1' of the output member and in particular the fuse holders 52, 53.

• - einerseits axial in Anlage am Mittelsteg 535 des Halters 53 und
• - andererseits durch die Mittelstege 525, 535 der Halter 52, 53 zentriert.

In particular, the sealing washer 58 passes axially through the output member and emerges axially on one side and on the other side of the fuse holders 52, 53. In this way the sealing washer 58 is:

• - On the one hand axially in contact with the central web 535 of the holder 53 and
• - Centered on the other hand by the central webs 525, 535 of the holders 52, 53.

In addition, the washer 58 is axially fixed with respect to the output member 5B. The sealing disk 58 is centered by the central windows 526, 536 of the holders 52, 53 so that the receptacle 93 is limited.

In this embodiment, the sealing washer 58 has a continuous and arcuate shape, particularly embodied in a stepped shape. In particular, the additional end 90 is radially offset with respect to the remainder of the washer 58 to partially enclose the bearing 6 .

• - das Drehmomentausgangsorgan 5B außerdem eine Beilagscheibe 59 aufweist, die insbesondere mit den ersten Befestigungsmitteln, hier einer Reihe von Nieten 71, fest mit den Sicherungshaltern 52, 53 verbunden ist;
• - die Beilagscheibe 59 eine kontinuierliche oder diskontinuierliche Form um die Achse X hat, insbesondere segmentiert ist;
• - das zusätzliche Ende 90 durch Materialverformung, hier durch Tiefziehen oder Biegen hergestellt wir,
• - das zusätzliche Ende 90 in segmentierter Form durch Ausschneiden der Beilagscheibe 59 hergestellt werden kann;

In the 14 until 15 a fifth embodiment of the invention is described which is substantially similar to the first embodiment except that:

• the torque output member 5B also includes a washer 59 which is secured to the fuse-holders 52, 53, in particular by the first fastening means, here a series of rivets 71;
• the washer 59 has a continuous or discontinuous shape about the X axis, in particular it is segmented;
• - the additional end 90 by material deformation, we produced here by deep drawing or bending,
• - the additional end 90 can be made in segmented form by cutting out the washer 59;

In this fifth embodiment, the washer 59 is positioned between the end of the first fastener 71 and one of the fuse holders 52,53. The washer 59 is placed here between the head 711 of the rivets forming the first fastening means 71 and the fuse holder 52 with the smaller outside diameter DS2.

For example, the shim 59 may be formed of sheet metal segments that are angularly spaced from one another, such as two angularly spaced from one another.

In addition, the washer 59 consists of a number of axially stacked layers, in particular sheet metal layers, here two, as in 14 shown.

In addition, the washer 59 extends radially between an inner diameter DM1 and an outer diameter DM2. In this embodiment, the inside diameter DM1 of the washer 59 is smaller than the inside diameter DS1, DS1' of the output member and in particular the fuse holder. In 14 the outside diameter DM2 of the washer 59 is greater than the outside diameter DS2, DS2' of the output member and in particular the fuse holder. Thus, the washer 59, and in particular its outside diameter DM2, can be centered on the radially outer end of one of the fuse holders.

In addition, the washer 59 rests axially on the central web 525 of the fuse holder 52 and in particular on the side surface on the motor side. In addition, the washer can be flexible or rigid.

• - durch Tiefziehen ein Hohlraum 930, der die Aufnahme 93 teilweise begrenzt;
• - durch Tiefziehen ein Zentriermittel 592, das radial an der Flanke 530 des Halters 52 anliegt.

It is possible to realize several successive deformations for such a locking component 9 . These deep drawn sections form a stepped shape of the washer 59. In particular, the following can be produced:

• a cavity 930 partially delimiting the seat 93 by stamping;
• - By stamping a centering means 592 which abuts radially on the flank 530 of the holder 52.

The cavity 930 is also delimited by the axial bearing surface 931 and a centering pad 932 . The axial bearing surface 931 and the centering pad 932 can have continuous or discontinuous shapes about the X axis.

• - die Arretierkomponente zumindest durch einige der ersten Befestigungsmittel 71 gebildet wird, hier eine Reihe von Befestigungsnieten, von denen Axialarretiernieten für das Lager 6 gebildet werden.
• - das zusätzliche Ende 90 durch Materialverformung hergestellt wird, hier durch Materialverlängerung 7110;
• - das zusätzliche Ende 90 durch maschinelle Bearbeitung hergestellt werden kann, um die Materialverlängerung 7110 zu schleifen.

In 16 a sixth embodiment of the invention is described which is substantially similar to the first embodiment except that:

• the locking component is constituted by at least some of the first fastening means 71, here a series of fastening rivets from which axial locking rivets for the bearing 6 are formed.
• - the additional end 90 is made by material deformation, here by material elongation 7110;
• - the additional end 90 can be machined to grind the material extension 7110.

In this fifth embodiment, the additional end 90 of an axial locking rivet is in the form of a rivet head. Therefore, the extra end 90 and the head 711 protrude radially inward towards the bearing 6.

Preferably, the lengthening of the material is carried out at the level of the heads 711 of the axial locking rivets, so that they differ from the other fastening rivets in the series forming the first fastening means 71.

Furthermore, of the first fastening means 71, the heads of the locking rivets have a larger diameter than the heads of the other rivets in the same row. In addition, the heads of the locking rivets have a larger diameter than the heads of the rivets forming the second fastening means 72.

Furthermore, of the first fastening means 71, the head of the locking rivets is greater in height than the head of the other rivets in the same row. In addition, the head of the locking rivets is greater in height than the head of the rivets forming the second fastening means 72.

The locking component 9 consists in particular of pairs of locking rivets evenly distributed angularly about the axis X and interposed in particular between other rivets forming the row of rivets.

For example, eight locking rivets form the locking component 9, with four pairs of locking rivets being angularly evenly distributed. As a variant, the series consists entirely of axial locking rivets forming the locking component 6. All of the axial locking rivets can then form the first fasteners.

In 16 the additional end of such axial locking rivets is machined to give it its final shape.

A cavity 930 can thereby be formed. The cavity 930 of an axial locking rivet is delimited by the axial bearing surface 931 and a centering pad 932, both of which have a discontinuous shape about the X axis.

It remains possible, according to variants of the invention, to produce rivet heads with a circular or polygonal, in particular hexagonal, square or even rectangular cross-section, provided that the diameter or the largest transverse dimension of this cross-section is compatible with the dimensions of the limiter and rolling element components.

• - Das zusätzliche Ende 90 der Arretierkomponente kann durch das Drehmomentausgangsorgan B definiert sein.
• - Die gesamte Axialarretiervorrichtung 6' ist mit Verriegelungsmitteln 61R, 62R, 62R' und Zentriermitteln 61C, 62C, 62C' fest am Primärschwungrad 2 angebracht, insbesondere am ringförmigen Abschnitt 22 oder an der primären Nabe 25 und/oder am Deckel 24. So kann das Sekundärschwungrad 3 auf dem Primärschwungrad 2, z.B. auf dem ringförmigen Abschnitt 22, mittels der Axialarretiervorrichtung 6' arretiert und geführt werden. Diese sorgt für eine axiale Arretierung, wenn die relative Bewegung von Primär- und Sekundärschwungrad zueinander das zulässige Axialspiel überschreitet.

the 17 until 27 Figure 12 shows further embodiments of the invention which are substantially similar to the first embodiment, with the exception that the rolling member is replaced by an axial locking device 6'.

• - The additional end 90 of the locking component can be defined by the torque output member B.
• - The entire axial locking device 6' is fixedly attached to the primary flywheel 2, in particular to the annular portion 22 or to the primary hub 25 and/or to the cover 24, by means of locking means 61R, 62R, 62R' and centering means 61C, 62C, 62C' The secondary flywheel 3 is locked and guided on the primary flywheel 2, for example on the annular section 22, by means of the axial locking device 6'. This ensures axial locking when the relative movement of the primary and secondary flywheels exceeds the permissible axial play.

• - auf einer sogenannten vorderen Seite das zusätzliche Ende 90 der Arretierkomponente, insbesondere des Ausgangsorgans 5B, und
• - auf einer anderen, sogenannten hinteren Seite AR das Sekundärschwungrad 3, insbesondere die Nabe 35 des Sekundärschwungrads.

In the illustrated examples, the axial locking device 6' locks axially

• - on a so-called front face, the additional end 90 of the locking component, in particular of the output member 5B, and
• - on another, so-called rear side AR, the secondary flywheel 3, in particular the hub 35 of the secondary flywheel.

The axial locking device 6' has a centering piece 61' in the manner of a guide washer from which the torque output member 5B of the torque limiter is centered directly or indirectly.

• - einen sogenannten radial äußeren Abschnitt 61C, der Folgendes bilden kann:
• - Zentriermittel 61C zum radialen Zentrieren einer Hysteresekassette 60' oder des Ausgangsorgans 5B;
• - Verriegelungsmittel 61R zum Arretieren des Drehmomentbegrenzers und insbesondere des zusätzlichen Endes 90;
• - Verriegelungsmittel 61R, um fest mit dem Primärschwungrad 61 verbunden zu werden, hier durch eine Reihe von Nieten;

In the illustrated examples, this centering piece 61 has:

• - a so-called radially outer portion 61C, which can constitute:
• - centering means 61C for radially centering a hysteresis cassette 60' or the output member 5B;
• locking means 61R for locking the torque limiter and in particular the additional end 90;
• - locking means 61R to be fixed to the primary flywheel 61, here by a series of rivets;

As an example for the 18 , 20 the centering piece 61' can be designed in a conical shape.

As an example for the 17 , 19 , 21 the centering piece 61' can be designed in a stepped form. The locking means 61R are then radially offset from the radially outer portion 61C.

the 17 until 18 show an axial locking device 6' comprising an axial stack of at least two discs arranged between the primary flywheel 2 and the secondary flywheel 3, in particular with the secondary hub 35.

19 Figure 13 illustrates an axial locking device 6' with at least one axial stack of at least two discs located between the primary flywheel 2 and the torque limiter.

The axial stack of discs in the 17 until 19 also includes the centering piece 61'.

Each axial locking device 6 'in the 19 and 22 until 27 comprises at least one hysteresis cassette 60', 60'' formed by a single spring washer 63' contained and centered with respect to one or two guide cage(s) 62', 62''. The conically shaped spring washer 63' of the Belleville type has, in cross-section, an angle of inclination α1 or α2 in relation to the at least one guide cage 62', 62".

• - auf der einen Seite in axialer Anlage an dem radial inneren bzw. äußeren Ende des Ausgangsorgans 5B und
• - auf der anderen Seite in axialer Anlage jeweils an ringförmigen Abschnitt 22 bzw. am Deckel 24 des Primärschwungrads angeordnet.

Each hysteresis cassette 60', 60" is:

• on one side in axial abutment with the radially inner and outer ends of the output member 5B and
• - Arranged on the other side in axial abutment respectively on the annular portion 22 and on the cover 24 of the primary flywheel.

• - einen Mittelsteg, auf dem das Drehmomentausgangsorgan 5B in anliegend angebracht ist;
• - mindestens ein Mittel zum Zentrieren der Federscheibe 63', das aus einem oder mehreren Zentrierrändern besteht, die zumindest auf dem Außendurchmesser jedes Führungskäfigs 62', 62" angeordnet sind.

Each guide cage 62', 62" also includes:

• - a central web on which the torque output member 5B is mounted in abutting manner;
• at least one means for centering the spring washer 63', consisting of one or more centering rims arranged at least on the outside diameter of each guide cage 62', 62''.

22 shows a first and a second hysteresis cassette 60', 60", which are arranged axially on one side and on the other side of the torque output element 5B. The hysteresis cassette 60' is attached to the additional end 90, here the radially inner end of the torque output element 5B and is referred to as the first hysteresis cassette.

As an example in the 22 until 24 and 27 For example, the first hysteresis cassette 60' comprises two coaxial guide cages 62' in which is inserted a spring washer 63' centered on the centering rims 62C. The centering rims 62C are located on the inner and outer diameters of each guide cage 62' so that they face each other axially. These rest against one another and delimit a space between the guide cages, the so-called minimum height, in which the spring washer 63' is accommodated.

By way of example, the two guide cages are connected to one another by locking means 62R of the snap-fit type. the 23 until 24 show this latching connection, which is realized by fitting tabs 620 of one guide cage through the windows 621 of another guide cage, in particular by positive locking. Advantageously, each guide cage has alternate tabs 620 and windows 621 angularly distributed about the X axis in an angular or regular distribution.

the 19 and 26 show a hysteresis cassette 60'' (second hysteresis cassette) mounted directly on the primary flywheel cover 24 and comprising a single guide cage 62'' and spring washer 63'. The spring washer 63' is inserted and centered between the guide cage 62" and the cover 24.

25 shows means 62R' for locking the guide cage 62" to the cover 24. Advantageously, the cover 24 has windows 240 through which the means 62R' for locking the guide cage 62" are fixedly attached, preferably in the form of a snap-fit connection created by assembly of tabs 620' of the guide cage through the windows 240 of the lid 24 is made.

26 shows means 62C' for centering the guide cage 62" with the cover 24. In contrast, the cover 24 has no windows or other material recess here, the centering pad 62C' of the guide cage 62" resting on the inner diameter of the cover 24. This centering support 62C' can be of the collar type, in the form of discontinuous portions passing through the windows 240 of the cover 24.

The second hysteresis cassette is in 27 replaced by an axial stack of spring washers 63', 64' placed between the cover 24 of the primary flywheel 2 and the torque output member 5B. This axial stack of discs 63', 64' forms in part the axial locking device 6'.

The first hysteresis cassette is in 19 replaced by an axial stack of plastic or spring washers 61', 64' interposed between the annular portion 22 of the primary flywheel and the torque output member 5B. This axial stack of discs 61', 64' forms in part the axial locking device 6'.

The use of the verb "comprise", "comprise" or "include" and its conjugated forms does not exclude the presence of elements or steps other than those specified in a claim. In the claims, any reference signs placed in parentheses shall not be construed as limiting the claim.

The dimensions given or illustrated may not be to scale and correspond only to a particular model of torque limiter developed by the applicant. The manufacturing method according to the invention is adapted to other nominal diameters of the restrictor and other thicknesses of its components as required.

QUOTES INCLUDED IN DESCRIPTION

This list of documents cited by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent Literature Cited

• EP 2886907 A1 [0008]
• FR 3011602 A1 [0008]

Claims (14)

Damping device (1) for a drive train, comprising: - a primary flywheel (2) with a central hub (29) which can be connected to a drive shaft, and a secondary flywheel (3) which can be rotated relative to one another about an axis (X), - a torsional damper (4) made up of elastic members (40) for transmitting torque and damping torsional irregularities between the primary flywheel (2) and the secondary flywheel (3), - a pre-assembled torque limiter (5) containing: a torque input member (5A) housing the elastic members (40), a torque output member (5B) connected to the secondary flywheel (3), and at least one sealing washer (58) firmly attached to the output member (5B), the torque limiter (5) having a locking component (9) selected from the output member (52, 53) and the sealing washer (58) and an additional end (90), the shape of which is adapted by deformation or removal of material from the locking component to accommodate a rolling element (6) or an axial locking device (6'), the secondary flywheel (3) being guided on the primary flywheel (2): - with the rolling element (6) partially mounted in the secondary flywheel (3) and held axially: on the one hand by the secondary flywheel (3) and on the other hand by the additional end (90) of the locking component (9), or - with the axial locking device (6') fixed to the primary flywheel and axially holding on the one hand the additional end (90) of the locking component and on the other hand the secondary flywheel (3). Damping device (1) after claim 1 , the additional end (90): - being formed by deep-drawing or bending the locking component (9), in particular from a single sheet metal, and/or - extending discontinuously in the circumferential direction around the axis X, in particular by cutting out a plurality of locking segments (91 ) in the form of locking projections, lugs, tabs or tabs. Damping device (1) after claim 1 or 2 , the torque input member (5A) having a central window (516) in which the torque output member (5B) is partially mounted, the torque output member (5B) further having another central window (526, 536) in which the rolling member (6th ) or the axial locking device (6') is partially attached. Damping device (1) according to any one of the preceding claims, in which the additional end (90) of the locking component (9) delimits an internal housing (93) in which the rolling element (6) or the axial locking device (6') is at least partially housed. Damping device (1) after claim 4 wherein the receptacle (93) is made by removing material (93) from the additional end (90), the removal of material being between 2/3 and 9/10 of the original thickness of the additional end (90), in particular by Machining a cavity (93) in the extra end (90). Damping device (1) according to one of the preceding claims, wherein the locking component (9) is formed by the sealing washer (58), the additional end (90) by material deformation starting from the inner diameter (DF1) of the sealing washer (58), in particular by deep drawing or bending. Damping device (1) according to one of the preceding claims, wherein the pre-assembled torque limiter (5) has the following: - a drive washer (51) constituting the input member (5A) and capable of receiving the elastic members (50), - two drive plate fuse-holders (52, 53) cooperating frictionally with the drive plate, the fuse-holders (52, 53) being assembled to form the input member (5A). Damping device (1) according to the preceding claim, in which the torque output member (5B) further comprises a washer (59) of continuous or segmented form, the locking component (9) being constituted by the washer (59), the washer (59) being formed by first fastening means (71), such as a series of rivets, is fixedly connected to the fuse holders (52, 53). Damping device (1) according to one of Claims 1 until 5 combined with claim 7 , the locking component (9) being formed by the fuse holder (52) which is axially furthest away from the secondary flywheel (3), the additional end (90) being formed by material deformation of the inner diameter (DS1) of the fuse holder (52), in particular by deep-drawing and /or machining. Damping device (1) according to one of Claims 1 until 5 combined with claim 7 , wherein the fuse holder (52, 53) and you washer (58) are connected by a series of rivets forming first fastening means (71), the locking component (9) is formed by at least some of the rivets of the series, the additional end (90) being formed by material deformation of the head (711) of these rivets is made. Damping device (1) according to one of the preceding claims, wherein the axial locking device (6') consists of at least the following elements: - a centering piece (61') integral with the primary flywheel (2) and from which the torque output member of the torque limiter is centered directly or indirectly; and or - a hysteresis cartridge (60', 60") formed by at least one guide cage (62', 62") and a spring washer (63') which is inclined at an angle (α1, α2) with respect to the guide cage (62' , 62") is conically shaped, and which is arranged between the primary flywheel (2) and the torque output member (5B) of the torque limiter (5); and/or - an axial stack of discs (61', 62', 63', 64') placed between the primary flywheel (2) or secondary flywheel (3) on the one hand and the torque output member (5B) of the torque limiter (5) on the other. Damping device (1) according to the preceding claim, wherein the axial locking device (6') comprises two hysteresis cassettes (60', 60"), which are arranged axially on one side and on the other side of the torque limiter (5), which in particular are axially free of play on torque output element (5B) of the torque limiter. Damping device (1) after claim 11 or 12 wherein the at least one hysteresis cassette (60', 60") of the axial locking device (6') comprises: - a spring washer (63') inserted between two coaxial guide cages (62') mounted one above the other and preferably interlocked with each other connected, one of the guide cages being accommodated in a material recess of the additional end (90) of the locking component; or - a spring washer (63') which is connected between a single guide cage (62") and a cover (24) of the primary flywheel (2) is inserted, the guide cage (62'') being partially attached to the cover (24), preferably by a collar-type centering support (62C') or by locking means (62R') of the snap-in type. Damping device (1) for a drive train, comprising: - a primary flywheel (2), which may be connected to a drive shaft, and - a secondary flywheel (3) which can be rotated relative to one another about an axis (X), - a torsional damper (4) comprising: elastic members (40) for transmitting torque and damping torsional irregularities between the primary flywheel (2) and the secondary flywheel (3), - a pre-assembled torque limiter (5) containing: a torque input member (5A) housing the elastic members (40), a torque output member (5B) connected to the secondary flywheel (3), and at least one sealing washer (58) fixed to the output member (5B), the damping device (1) further comprising an axial locking device (6') constituted by at least one hysteresis cartridge (60', 60"), from which the output member (5B) of the torque limiter (5) relative to the primary flywheel (2nd ) is guided, the at least one hysteresis cassette (60', 60'') being firmly connected to the primary flywheel (2) by means for locking (60R, 62R, 62R') and for centering (60C, 62C, 62C').

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