DE102018103480A1 - Swivel element for pivotally receiving a damper device - Google Patents

Abstract

The invention relates to a pivoting element (1) for pivotally receiving a damper device (3) of a belt transmission (4), comprising at least the following components:
- A holding element (5) which is connectable to a housing element (6) of a belt transmission (4), wherein the holding element (5) has a first axial stop (8);
- A bearing element (10) which is axially feasible connected to the holding element (5), wherein the bearing element (10) has a second axial stop (9), wherein the first axial stop (8) and the second axial stop (9) has a predetermined axial distance (11) to each other, so that a damper device (3) with a predetermined axial clearance (12) between the two axial stops (8,9) is axially storable. The pivoting element (1) is mainly characterized in that the holding element (5) has a mounting stop (13) and the bearing element (10) has a corresponding counter-stop (14), wherein the mounting stop (13) and the counter-stop (14) in a state in which a belt transmission (4) is held in contact, in such a manner that the predetermined axial distance (11) is set.
Despite the bipartite, the pivoting element proposed here makes possible a very good use of space for a stiff damper device.

Description

The invention relates to a pivoting element for pivotally receiving a damper device of a belt transmission, a belt transmission with such a pivoting element, a drive train with such a belt transmission, and a motor vehicle with such a drive train.

A belt transmission, also referred to as a belt pulley or continuously variable transmission, for a motor vehicle, the belt pulley comprises at least one first pair of cones arranged on a first shaft and a second pair of cones arranged on a second shaft, and one for torque transmission between the pairs of conical pulleys provided wrapping means. A conical disk pair comprises two conical disks, which are aligned with corresponding conical surfaces towards each other and are axially movable relative to each other.

Such a belt transmission regularly comprises at least a first pair of conical disks and a second pair of cones, each with a first conical disk displaceable along the shaft axis, also referred to as a loose disk or travel disk, and a second conical disk fixed in the direction of the shaft axis, also referred to as a fixed disk, the torque transmission between As a result of a relative axial movement between the loose disk and the stationary disk, the belt means provided on the conical disk pairs run on a changeable active circle, that is to say with a variable running radius, as a result of the conical surfaces. As a result, a different speed ratio and torque ratio of a cone pulley pair on the other cone pulley pair is infinitely adjustable.

Such belt transmissions have long been, for example from the DE 100 17 005 A1 , known. During operation of the belt transmission, the wrapping means is thus displaced by means of the relative axial movement of the conical disks on the conical disk pairs between an inner position (small active circle) and an outer position (large active circle) in a radial direction. The wrapping means forms between the two conical disk pairs each a strand, wherein each configuration according to the direction of rotation of the cone pulley pairs, one of the strands forms a Zugtrum and the other strand a Schubtrum or a load strand and an empty strand.

In such belt transmissions, at least one damper device is provided in the installation space between the conical disk pairs. Such a damper device can be arranged on the traction strand and / or on the Schubtrum of the belt and serves to guide and thus to limit vibrations of the belt. Such a damper device is to be interpreted in terms of an acoustically efficient traction means (Umschlingungsmittelführung). The length of the system for guiding the belt and the stiffness of the damper device are decisive influencing factors. A damper device is designed, for example, as a sliding shoe or as a sliding guide with only one-sided, usually space-related (transversal to the belt means) on the inside, ie between the two Trumen, contact surface. Alternatively, the damper device is designed as a slide rail or with a contact surface on both sides, that is to say both on the outside, ie outside the looping circle formed, and on the inside contact surface with the respective run of the looping means.

The damper device is mounted by means of a pivot bearing with a pivot axis, whereby a pivoting of the damper device is made possible around the pivot axis. In some applications, the damper device is also transversely movable so that the damper device follows a (steeper oval) curve that deviates from a circular path about the pivot axis. The pivot axis thus forms the center of a (two-dimensional) polar coordinate system, the pivoting movement thus corresponds to the change of the polar angle and the transverse movement of the change of the polar radius. This superimposed, so superponed, translational movement of the pivoting movement is disregarded below for the sake of clarity. The pivot axis is aligned transversely to the running direction of the belt. This ensures that when adjusting at least one active circle of the belt drive, the damper device can follow the resulting new orientation of the belt. At the same time, the pivot bearing usually serves the axial guidance of the damper device and limits the movement of the damper device in the direction transverse to the running direction of the belt means by means of corresponding stop means, which are referred to here as axial stops. The pivot bearing is formed by means of a housing attached to the pivot member and a corresponding, the pivot member receiving recess on the damper device. The recess is referred to as a bearing receptacle. The pivoting element is often referred to as a holding tube, because in many applications it is made of a tube material.

Due to the assembly order of some belt transmissions, it is necessary to provide a two-piece pivoting element. A first part of the pivoting element is attached to the transmission housing and in a further, later assembly step, a second part is then attached to the first part. The first part is referred to here as a holding element and the second part as a bearing element. Subsequently, the assembly of the damper device takes place between the two axial stops. In a further assembly step, a housing cover is applied. Although the housing cover secures the second bearing element against falling out, however, a certain amount of play between the two parts of the pivoting element is tolerated (cf. 1 ). Between the first and the second part an anti-rotation device is preferably provided, whereby space is obtained by the stop means with an extension alone to the damper device or the bearing holder are executable.

The two parts of the pivoting element are thus so freely movable against each other on a predetermined length in the axial direction. This axial clearance, also referred to as stroke, is due to the tolerances of the transmission housing, the housing cover and two-part pivot element itself. The axial clearance between the two parts of the pivot member has a detrimental effect on the damper assembly space. The clearance causes the distance between the two axial stops is not constant. Thus, under certain circumstances, an axial movement of the damper device, which is larger than a one-part embodiment, is permitted. In addition, in some embodiments, a lubricating oil flow and / or cooling oil flow for the conical disk pairs guided by the pivoting element forces the two parts of the two-part pivoting element apart. In such an embodiment, in addition to the tolerance clearance, an increased axial safety distance to the nearby components such as conical disks and housing must be provided. This results in a given space less space for the damper device. As a result, the damper device is executable only with a reduced rigidity as compared to a damper device having a one-piece pivot member. Since the stiffness of a damper device greatly influences its damping properties, however, so that the acoustics of the transmission is deteriorated.

On this basis, the present invention has the object, at least partially overcome the known from the prior art disadvantages. The features of the invention will become apparent from the independent claims, to which advantageous embodiments are indicated in the dependent claims. The features of the claims may be combined in any technically meaningful manner, and to this end, the explanations of the following description and features of the figures may be used, which include additional embodiments of the invention.

• - ein Halteelement, welches mit einem Gehäuseelement eines Umschlingungsgetriebes verbindbar ist, wobei das Halteelement einen ersten Axialanschlag aufweist;
• - ein Lagerelement, welches axial aufführbar mit dem Halteelement verbunden ist, wobei das Lagerelement einen zweiten Axialanschlag aufweist,

wobei der erste Axialanschlag und der zweite Axialanschlag einen vorbestimmten Axialabstand zueinander aufweisen, sodass eine Dämpfervorrichtung mit einem vorbestimmten Axialspiel zwischen den beiden Axialanschlägen axial lagerbar ist. The invention relates to a (multi-part) pivoting element for pivotally receiving a damper device of a belt transmission, comprising at least the following components:

• - A holding element, which is connectable to a housing element of a belt transmission, wherein the holding element has a first axial stop;
• a bearing element, which is connected in an axially executable manner to the retaining element, the bearing element having a second axial stop,

wherein the first axial stop and the second axial stop have a predetermined axial distance from each other, so that a damper device with a predetermined axial clearance between the two axial stops is axially storable.

The pivoting element is mainly characterized in that the holding element has a Montieranschlag and the bearing element has a corresponding counter-stop, wherein the mounting stop and the counter-stop are mounted in a Umschlingungsgetriebe in touching contact, in such a manner that the predetermined axial distance is set.

In the following, reference will be made to the aforementioned pivot axis, if the axial direction, radial direction or the direction of rotation and corresponding terms are used without explicit reference.

To avoid the disadvantages mentioned and to provide the maximum installation space for the damper device with a two-part pivoting element, it is proposed to reduce the freedom of movement between the two holding ear parts as much as possible.

The belt is preferably loaded purely on train as a chain, as a belt or purely loaded on thrust designed as a push belt. Particularly preferably, the belt is designed as purely loaded on train link chain.

The pivoting element proposed here is provided for a belt transmission, in which due to the required assembly sequence, the pivoting element at least two parts must be executed. That is, with a first axial stop on a first part, here referred to as a holding element, and a second corresponding axial stop on a second, later mountable part, which is referred to here as a bearing element. The number of parts of the pivoting element is greater than two for some embodiments, so that the pivoting element can be regarded as a multi-part. However, the holding element and the bearing element form the main components, wherein the holding element is connectable in a first step with a housing element and in a second or later step, the bearing element is connectable to the holding element. From this point of view, the pivoting element is also referred to as a two-part pivoting element.

The required installation space of the pivoting element proposed here is embodied such that the pivoting element proposed here does not have to be modified without conversion measures on the belt transmission, and in particular the fastening device for the retaining element on a housing element. This fastening device for the retaining element and a corresponding retaining tab of the retaining element is preferably carried out conventionally, in which case the housing element is the gear housing. Alternatively, the housing element is a housing cover or another separate component of the transmission housing.

The holding element thus has a first axial stop, wherein this is formed separately or integrally with the holding element. Preferably, the first axial stop is rotationally fixed with respect to the pivot axis, so that the axial stop has a corresponding axial extent only for the entire pivot range of a recorded damper device, so that the pivot member by means of the first axial stop in a (first) axial direction, with respect to the housing element, with which is connected to the holding element in the assembled state, limits an axial movement of the damper device.

The mounted damper device is a sliding guide or a slide rail and has a bearing receptacle which, applied on the pivoting element, enables pivoting of the at least one sliding surface of the damper device about the pivot axis.

Furthermore, the pivoting element comprises the bearing element, which can be performed axially on the holding element for mounting. The bearing element comprises a corresponding second axial stop which limits an axial movement of the damper device, for example a slide rail or a sliding guide, in the opposite direction, ie in the (second) axial direction away from the housing element to which the holding element is fastened in the assembled state. The second axial stop is identical in its extension, and preferably in its overall shape, to the first axial stop. Also, the second axial stop is formed separately or integrally with the bearing element. If the two axial stops have a radial extent limited relative to the pivot axis and the bearing element is mounted as intended on the retaining element, then the two axial stops extend in the same radial direction, namely towards the guided run. With a limited radial extent is meant that a respective axial stop in the circumferential direction is not the same, that is not circular, is formed, but for example, a segment, for example, forms an angle of 40 ° of a circle.

The first axial stop and the second axial stop have a predetermined axial distance from each other, so that the damper device is mounted axially with its bearing receptacle with a predetermined axial play between the two axial stops. Such an axial clearance is to be set up in a belt transmission with a fixed disk and a loose disk such that the damping device can follow the axial migration of the belt in a changing transmission ratio. The axial migration of the belt is for example 15 mm [fifteen millimeters]. The axial clearance therefore corresponds to this amount of axial migration. The axial play limits the maximum width of the damper device but is not superimposed here by a tolerance game. Therefore, the damper device or its bearing mount with a maximum possible width and thus with a maximum possible stiffness in the available axial space executable.

This efficient space utilization is achieved in that the holding element has a Montieranschlag and the bearing element has a corresponding counter-stop.

The mounting stop and the counter-stop are held in touching contact (permanently) in the mounted state. This means that there is no tolerance-related axial clearance between the mounting stop and the counter-stop, but the mounting stop and the counter-stop are permanently in contact with one another in the installed state. Thus, in the design of the axial distance and / or the width of the bearing support of the damper device no tolerances for the gear housing and the housing cover are provided.

In all the embodiments mentioned here is preferably the Montieranschlag and the Counter stop formed as close to the second axial stop, so that no long tolerance chain forms and a tolerance-related extension or reduction of the desired axial distance for the bearing support of the damper device is negligible.

According to an advantageous embodiment of the swivel element, the bearing element is axially supportable by means of a spring element with a spring force against a housing element, so that mounted in a belt drive state of the mounting stop and the counter-stop are held in touching contact by means of the spring force.

In this advantageous embodiment, a spring element is provided, for example a helical compression spring, which braces the bearing element axially braced against a second housing element, for example a housing cover. With the spring force resulting from the tension, the spring element holds the mounting stop and the counter-stop (permanently) in touching contact together.

In one embodiment, in which lubricant and / or coolant, is supplied by the holding element and / or by the bearing element and a corresponding opening in the pivot member to the interior of the transmission housing, the spring force is set up so that they with the largest tolerance-related distance between the bearing element and the respective (second) housing element is greater than the (opposing) axial force resulting from the oil pressure on the bearing element, which thus presses apart the mounting stop and the counter stop. In this case, in comparison to a conventional embodiment, only the conventional mounting stop of the (second) housing element is replaced by a spring element and a (new) mounting stop of the retaining element thereby brought into touching contact with the (new) counter-stop and held in this position (permanently). Incidentally, the pivoting element and the transmission housing is preferably designed conventionally.

• - eines Niets, bevorzugt eines Blindniets;
• - einer Schraubgewindepaarung;
• - eines nach Aufbringen des Lagerelements auf dem Halteelement kalt-umgeformten Flanschs;
• - eines axial wirkenden Formschlusses, bevorzugt einer Schnappverbindung.

According to an advantageous embodiment of the pivoting element, the bearing element is connected to the retaining element by means of a tensile force acting axially with a tensile force such that the mounting stop and the counterstop are held in touching contact by means of the tensile force, wherein the traction device is preferably formed by means of one of the following components:

• a rivet, preferably a blind rivet;
• - a screw thread pairing;
• - A after application of the bearing element on the holding element cold-formed flange;
• - An axially acting positive connection, preferably a snap connection.

In this embodiment, a support against a housing member (with a compressive force) is not provided, but a tensile force is generated, which connects the holding member and the bearing member such that the mounting stop and the corresponding counter-stop are held in the mounted state permanently in touching contact.

In one embodiment, a rivet is provided. In one embodiment, the rivet is inserted transversely to the pivot axis. Preferably, the rivet is at an end face of the holding member and the bearing element, that is, a surface which is aligned towards the (second) housing element, for example, parallel thereto. This facilitates the assembly. For this purpose, the holding element forms a suitable undercut, behind which the rivet, preferably designed as a blind rivet, engages.

In another embodiment, a Schraubgewindepaarung is provided. In one embodiment, for example, a screw is introduced transversely to the pivot axis and arranged a lock nut opposite. Preferably, the pairing is arranged on the front side, whereby a good accessibility is provided during assembly. The thread is preferably attached to the holding element and the screw, for example a screw, is designed as a separate component. This separate embodiment is necessary when the second axial stop needs to be aligned with the first axial stop due to its circumferentially limited extent.

According to a further embodiment, a flange is formed after the bearing element has been applied to the retaining element, wherein preferably a tab or an edge of the retaining element after application of the bearing element, for example 90 °, for example in the manner of a rivet is bent radially outward.

In another embodiment, a positive connection is formed, wherein the bearing element engages behind an undercut on the holding element. Particularly preferably, this form-fitting is formed by means of a snap connection, which results in easy assembly but also easy disassembly, which can be carried out quickly and preferably without tools. The positive connection with an axial force component is preferred formed so that the Montieranschlag is pressed against the counter-attack and without further action, these two attacks are free of play together.

According to an advantageous embodiment of the pivoting element, the traction means is formed by means of a bolt fastened to the holding element with a threaded shank and a threaded nut, wherein the threaded nut acts against the counter-stop on the back, so that the counter-stop is pressed against the mounting stop.

In a preferred embodiment, preferably when the holding element is designed as a holding tube, is a bolt with a threaded shaft axially in the holding element or on the holding element, for example by means of positive engagement, for example a bayonet with reversal, by means of adhesion, such as screwing, or material bond, such as gluing , Soldering or welding, fixed such that the threaded shaft has axially to the bearing element. After mounting the bearing element on the retaining element, the bearing element is axially fixed by means of a threaded nut.

According to an advantageous embodiment of the pivot member, the bearing element integral with the second axial stop on an axial element, wherein the axial element forms a bearing seat with a predetermined axial distance corresponding axial extent for a damper device, wherein preferably the second axial stop relative to the first axial stop by means of one of the Axialelement and the holding element, particularly preferably the first axial stop, formed against rotation is secured against relative rotation about the pivot axis.

The axial element forms the bearing seat for the bearing seat of the male damper device and has for this purpose an axial extent, which has the predetermined axial distance for the male bearing mount of the damper device.

In one embodiment, the bearing element in addition to the counter-stop comprises only the second axial stop and optionally further elements for securing the bearing element to the holding element. Then, an axial element is additionally provided, which is formed separately from the bearing element. The axial element can be applied to the holding element before assembly of the bearing element or forms part of the holding element. Alternatively, the separate axial element can be connected to the bearing element before the bearing element is mounted on the retaining element.

Preferably, the axial element, if it is formed separately with a bearing seat forming the axial extent, which corresponds exactly to the predetermined axial distance, so that a continuous bearing surface for the bearing seat of the damper device is formed. Alternatively, an axial play is provided and / or a part of the bearing seat is formed by the holding element and / or by the bearing element.

In a preferred embodiment, the axial element and also the second axial stop are formed integrally with the bearing element. This does not exclude that the components of the bearing element are made separately and are joined together in one or more subsequent steps prior to assembly with the holding element.

Preferably, the components of the bearing element, if they are made separately, joined together in a material fit. In this embodiment, the number of parts is reduced, so that the assembly is easy and quick to carry out.

In a preferred embodiment, the second axial stop is secured by means of the axial element against relative rotation with respect to the first axial stop. For example, a corresponding rotation is formed by the axial element is mounted secured to the holding member against relative rotation. Such a distribution assurance is accomplished, for example, by means of an ovality of a connector. In a preferred embodiment, the first axial stop forms a depression, which forms a non-circular receptacle for a corresponding element of the axial element. For example, a circular receptacle, preferably formed as a recess in the first axial stop, wherein on at least one side of a flattened segment is formed in an otherwise circular shape. The axial element then has a corresponding insertion geometry for this purpose. In this case, an axial play is preferably provided, wherein the Montieranschlag and the counter-stop are formed axially close to the second axial stop. As a result, the formation of a double fit is avoided and at the same time a very short or negligible tolerance chain is formed.

• - eine Getriebeeingangswelle mit einem ersten Kegelscheibenpaar;
• - eine Getriebeausgangswelle mit einem zweiten Kegelscheibenpaar;
• - ein Umschlingungsmittel, mittels welchem das erste Kegelscheibenpaar mit dem zweiten Kegelscheibenpaar mit veränderbarer Übersetzung drehmomentübertragend verbunden ist;
• - eine Dämpfervorrichtung, wobei die Dämpfervorrichtung zum Dämpfen des Umschlingungsmittels zumindest einseitig transversal an dem Umschlingungsmittel anliegt;
• - ein Getriebegehäuse umfassend zumindest ein erstes Gehäuseelement, wobei das Getriebegehäuse die Kegelscheibenpaare, das Umschlingungsmittel und die Dämpfervorrichtung einhaust; und
• - ein Schwenkelement nach einer Ausführungsform gemäß der obigen Beschreibung für die Dämpfervorrichtung, wobei das Schwenkelement an dem ersten Gehäuseelement derart befestigt ist, dass die Dämpfervorrichtung an dem Umschlingungsmittel anliegend und auf dem Schwenkelement verschwenkbar gelagert ist.

According to a further aspect, the invention relates to a belt drive for a drive train, comprising at least the following components:

• - A transmission input shaft with a first cone pulley pair;
• - A transmission output shaft with a second cone pulley pair;
• - a looping means, by means of which the first conical disk pair is connected to transmit torque to the second conical disk pair with variable transmission;
• - A damper device, wherein the damper device for damping the belt means abuts at least on one side transversely to the belt means;
• a transmission housing comprising at least a first housing element, wherein the transmission housing einhaust the conical disk pairs, the belt and the damper device; and
• a pivoting element according to an embodiment according to the above description for the damper device, wherein the pivoting element is fastened to the first housing element in such a way that the damper device is mounted on the belting means and pivotably mounted on the pivoting element.

With the belt transmission proposed here, torque can be transmitted from a transmission input shaft to a transmission output shaft and, conversely, translating or reducing, the transmission being infinitely variable at least in regions. A belt transmission is for example a so-called CVT (continuous variable transmission). The wrapping means is, for example, a multi-membered chain. The belt is displaced on conical pulley pairs in opposite directions from radially inward to outward and vice versa, so that sets on a respective pair of conical pulleys, a circle of activity with a changed radius of rotation. From the ratio of the active circuits results in a translation of the torque to be transmitted. The two active circles are connected to each other by means of an upper and a lower strand, namely a load strand, also called the traction strand or shear strand, and an empty strand of the belting means.

Ideally, the strands of the belt form a tangential alignment between the two active circles. This tangential orientation is superimposed by induced vibrations, for example caused by the finite division of the belt and as a result of the early leaving of the active circuit due to the escape acceleration of the belt.

The damper device is set up to abut with its at least one sliding surface on a corresponding abutment surface of a strand to be damped, for example of the load tube, such that such vibrations are suppressed or at least damped. This effect is reinforced in a damper device which (transversely) has a sliding surface on both sides of the strand to be damped. Furthermore, for an application, a transverse guide, that is to say in a plane parallel to the formed loop of the belt, is provided on one or both sides with a guide surface. This forms a sliding channel. The strand is thus guided in a plane parallel to the at least one sliding surface and the running direction of the strand is in this parallel plane. For the best possible damping, the sliding surface is designed as close as possible to the strand of the belt. For this purpose, the sliding surface must be made as stiff as possible. The rigidity can be improved by means of the width of the sliding surface transverse to the running direction of the belt.

So that the damper device can follow the movement of the strand, a pivot bearing is provided, on which the damper device is seated with its pivot receiver.

The belt transmission proposed here has a gearbox housing, which requires due to the mounting sequence that the pivoting element is made in two parts. The pivoting element proposed here can easily be used in a conventional transmission housing, wherein preferably no adjustments to the transmission housing are necessary in comparison to a conventional design. However, compared to the conventional embodiment, the pivoting element has the advantage that the axially available installation space for the damper device can be fully utilized without this having to be maintained by a tolerance tolerance. In a preferred embodiment, less material is also required, for example, by eliminating an axial spacer to a (second) housing element.

According to a further aspect, the invention relates to a drive train, comprising a drive unit with an output shaft, at least one consumer and a belt transmission according to one embodiment as described above, wherein the output shaft for torque transmission by means of the belt drive with the at least one consumer with variable transmission is connectable.

The drive train is set up to transmit a torque provided by a drive unit, for example an internal combustion engine or an electric motor, and output via its drive shaft for use as needed, ie taking into account the required rotational speed and the required torque. One use is, for example, an electrical generator for providing electrical energy. To the torque targeted and / or by To transmit a gearbox with different ratios, the use of the belt drive described above is particularly advantageous because a large spread ratio is achieved in a small space and the drive unit with a small optimal speed range is operable. Conversely, a recording of an inertial energy introduced by, for example, a drive wheel, which then forms a drive unit in the above definition, can be implemented by means of the belt drive on an electric generator for recuperation, ie the electrical storage of braking energy, with a correspondingly established torque transmission train. Furthermore, in a preferred embodiment, a plurality of drive units are provided, which are connected in series or in parallel or decoupled from each other operable and their torque can be provided by means of a belt transmission according to the above description, each as needed available. Examples are hybrid drives of electric motor and internal combustion engine, but also multi-cylinder engines in which individual cylinders (groups) are switchable.

The belt transmission proposed here makes it possible to use a damping device which efficiently utilizes the existing installation space, so that very good damping properties can be achieved due to an increase in the rigidity of the damping device. Thus, the noise emissions of such a powertrain are reduced. Thus, the efficiency can be increased due to a reduction of the vibrations. In addition, reduced wear on the belt and thus the life of the belt drive can be extended.

According to a further aspect, the invention relates to a motor vehicle, comprising at least one drive wheel, which is drivable by means of a drive train according to an embodiment as described above.

Most motor vehicles today have a front-wheel drive and sometimes arrange the drive unit, for example an internal combustion engine and / or an electric motor, in front of the driver's cab and transversely to the main direction of travel. The radial space is especially small in such an arrangement and it is therefore particularly advantageous to use a belt drive small size. Similarly, the use of a belt transmission designed in motorized two-wheelers, for which a significantly increased performance is required with the same space.

This problem is exacerbated in passenger cars of the small car class according to European classification. The units used in a passenger car of the small car class are not significantly reduced compared to passenger cars larger car classes. Nevertheless, the available space for small cars is much smaller.

In the motor vehicle proposed here with the drive train described above, a low noise emission is achieved, so that a lesser effort in terms of sound insulation is required. For a smaller space requirement for the belt transmission is achieved. In addition, it is possible, alternatively or additionally, to set up a low noise emission and a long service life.

Passenger cars are assigned to a vehicle class according to, for example, size, price, weight and power, and this definition is subject to constant change according to the needs of the market. In the US market, cars of the class small cars and microcars are classified according to European classification of the class of Subcompact Car and in the British market they correspond to the class Supermini or the class City Car. Examples of the micro car class are a Volkswagen up! or a Renault Twingo. Examples of the small car class are an Alfa Romeo Mito, Volkswagen Polo, Ford Fiesta or Renault Clio.

• 1: ein konventionelles Schwenkelement in räumlicher Darstellung;
• 2: ein konventionelles Schwenkelement im Schnitt;
• 3: ein Schwenkelement mit einem ersten Federelement in räumlicher Ansicht;
• 4: ein Schwenkelement mit dem ersten Federelement im Schnitt;
• 5: ein Schwenkelement mit einem zweiten Federelement im Schnitt;
• 6: ein Federpin mit einem dritten Federelement in räumlicher Ansicht;
• 7: der Federpin im Schnitt;
• 8: ein Schwenkelement mit Niet in räumlicher Ansicht;
• 9: ein Halteelement mit Flansch in räumlicher Ansicht;
• 10: ein axial einzubringender Niet, ausgeführt als ein Blindniet, im Schnitt;
• 11: ein Schwenkelement mit Montieranschlag und Gegenanschlag ausgebildet für einen Niet im Schnitt;
• 12: ein Schwenkelement mit Schraubgewindepaarung in räumlicher Ansicht;
• 13: ein Halteelement mit Bolzen in räumlicher Ansicht;
• 14: ein Schwenkelement im Schnitt mit Schraubgewindepaarung;
• 15: schematisch ein Umschlingungsgetriebe mit Gleitschiene; und
• 16: ein Antriebsstrang in einem Kraftfahrzeug mit Umschlingungsgetriebe.

The above-described invention will be explained in detail in the background of the relevant technical background with reference to the accompanying drawings, which show preferred embodiments. The invention is not limited by the purely schematic drawings in any way, it being noted that the drawings are not dimensionally accurate and are not suitable for the definition of size ratios. It is shown in

• 1 : a conventional pivoting element in a spatial representation;
• 2 a conventional pivoting element in section;
• 3 a pivoting element with a first spring element in a spatial view;
• 4 a pivoting element with the first spring element in section;
• 5 a pivoting element with a second spring element in section;
• 6 a spring pin with a third spring element in a spatial view;
• 7 : the spring pin in section;
• 8th : a pivoting element with rivet in a spatial view;
• 9 : a holding element with flange in spatial view;
• 10 a rivet to be inserted axially, designed as a blind rivet, in section;
• 11 a swivel element with mounting stop and counter-stop formed for a rivet in section;
• 12 : a pivot element with screw thread pairing in a spatial view;
• 13 : a holding element with bolts in a spatial view;
• 14 : a pivoting element in the section with Schraubgewindepaarung;
• 15 schematically a belt drive with slide rail; and
• 16 : a drive train in a motor vehicle with belt drive.

Ordinal numbers used in the preceding and following description, unless explicitly stated to the contrary, are for the purpose of distinctness only and do not represent any order or ranking of the designated components.

In 1 is in spatial representation a conventional pivoting element 46 shown, which is a holding element 5 and a conventional bearing element 47 includes. The conventional pivoting element 46 has a pivot axis 2 on, to which the bearing seat 26 a pivoting of a damper device 3 (see 15 ). Axially, this is the damper device 3 by means of the first axial stop 8th , which here in one piece with the conventional holding element 5 is formed and the second axial stop 9 , which here in one piece with the conventional bearing element 47 is formed to an axial play 12 movably secured.

In 2 is the conventional pivoting element 46 , as in 1 shown, shown in section, wherein (shown purely schematically) here in the illustration on the right a first housing element 6 , For example, the transmission housing, and left a second housing element 7 , For example, a housing cover, are provided. On the camp seat 26 is purely schematically the bearing seat of a male damper device 3 (see 15 ), which axially within a predetermined axial distance 11 pivotable with a predetermined axial play 12 is stored. The axial distance 11 is between the first axial stop 8th and the second axial stop 9 educated. The holding element 5 is by means of a conventional retaining tab 45 on the first housing element 6 , preferably rotationally fixed, attached. The conventional bearing element 47 is here on the holding element 5 only attached axially. The conventional bearing element 47 forms towards the second housing element 7 a conventional mounting stop 48 , which with a conventional assembly game 44 to a conventional counter-attack 49 of the second housing element 7 is complained of. This conventional assembly game 44 is at the predetermined axial distance 11 aufaddieren, so that in the presence of a tolerance increased axial play 12 results.

In 3 is a pivoting element 1 shown in a spatial view, here for the sake of clarity, most of the components are identical to those of the conventional embodiment. In this respect, reference is made to the preceding description. This is the end of the bearing element 10 So pointing the way from the holding element 5 , a spring element 15 provided, which for exerting a spring force 16 against the second housing element 7 is braced supported. This is in the following 4 described in more detail.

In 4 is the pivoting element 1 according to 3 shown in section, it can be seen that the spring element 15 clamped on the second housing element 7 is supported. As a result, an axially towards the holding element 5 directed spring force 16 formed, which over one, preferably in comparison to a conventional spacer 50 shortened, spacers 50 the mounting stop 13 and the counter-attack 14 (permanently) touchingly keeps in touch. Here is the holding element 5 designed as a feeding element, via which a lubricant and / or coolant can be fed, which via an opening 52 is exhaustible. The spring force 16 This is greater than that as the opposite axial force resulting from the oil pressure 51 , By means of the spring element 15 is a tolerance match of the distance between the first housing element 6 and the second housing member 7 independently.

In 5 is pivoting element 1 similar to in 4 shown in section. In that regard, reference is made to the preceding description. Here is another configuration of a spring element 15 for applying a spring force 16 shown. The spring element shown here 15 is formed as a conical elastomer pin, which in a recess in the second housing element 7 introduced and supported axially braced against it. This depression also forms a radial bearing in cooperation with the elastomer pin 63 so the pivot bearing 1 here additionally stored radially. The elastomer pin is here (optional) on a screw 62 applied, for example by vulcanization, and the screw 62 is in an appropriate threaded receptacle 61 in the spacer 50 of the bearing element 10 added.

In 6 (spatial view) and in 7 (Sectional view) is an elastomer pin and the screw 62 according to 5 replacing spring pin 64 shown so that the spring pin 64 like the spring element 15 according to 4 or according to 5 , So with additional radial support in the radial bearing 64 of the second housing element 7 , works. The spring pin 64 includes a pin element 65 which is in a sleeve 66 is guided. The spring force 16 is of a spring element designed as a compression spring 15 on the pin element 65 exerted by the spring element 15 between the sleeve 66 and the pin element 65 is tense. The sleeve 66 is in a corresponding receptacle of the spacer 50 (see 5 ) Simply plugged, and optionally cohesively with the bearing element 10 connectable, or the sleeve 66 is screwed externally with a thread.

In 8th is a pivoting element 1 shown in a spatial view, pointing to a spacer 50 (see 1 to 5 ) can completely dispense, so that material can be saved. Incidentally, for the sake of clarity, the pivoting element 1 similar to the one described above 3 . 4 and 5 shown pivoting element executed. In this respect, reference is made to the preceding description. One-sided of the bearing element 10 So on the holding element 5 facing away, a receptacle for a rivet is provided. A suitable rivet is for example in 10 shown.

In 9 is that the representation in 8th corresponding retaining element 5 shown individually in a spatial view, with flanges here 20 to recognize which here undercuts for a rivet 18 or a snap closure 21 form.

In 10 is in three steps attaching a rivet 18 , here executed as blind rivet, shown in section. Here are two elements, so here the bearing element 10 and the flange 20 of the holding element 5 , in the first step a rivet 18 with a draw bolt 53 in the appropriately prepared recording (axially) introduced. Then the tension bolt is removed from the rivet in the following two steps 18 extended. As a result, the rivet (in the illustration) below the flange 20 deformed and thus radially widened. The tension bolt tears at a predetermined breaking point, so that the bearing element 10 and the holding element 5 now pulled together tightly together. The elements shown flange 20 and end wall of the bearing element 10 preferably form the Montieranschlag 13 and the counter-attack 14 (see 11 ).

In 11 is the pivoting element 1 as it is in 8th shown is shown in section, here the location of the rivet 18 as he is in 10 is shown, is designated. Thus, a tensile force 17 on the bearing element 10 exercised. At the first axial stop 8th is here as well as in the previous figures (optional) an anti-rotation 28 educated. In the anti-rotation device formed as a plug-in receptacle 28 An axial assembly game is provided so that there is no double fit and at the same time the Montieranschlag 13 and the counter-attack 14 close to the second axial stop 9 are arranged so that the tolerance chain is as short as possible. Alternatively shown instead of a rivet is a snap connection 21 formed, with a snap hook behind the flange 20 attacks. Here is also the axial element 25 from the second axial stop 9 of the bearing element 10 formed separately, with a rotation 28 of the second axial stop 9 opposite the first axial stop 8th by means of a two-sided anti-rotation 28 of the axial element 25 is formed. The axial element 25 here has an axial extent 27 on, which with the desired axial distance 11 , where applicable, minus a necessary assembly tolerance, is identical.

In the 12 to 14 a variant is shown in which the retaining element 10 by means of a screw thread pairing 19 axially with the retaining element 5 connected is. Incidentally, the pivoting element shown here 1 with the pivoting element 1 according to the 8th to 11 identically formed.

In 13 is to realize that a bolt 22 of which only one to the second axial stop 9 pointing threaded shaft 23 to see which in the holding element 5 introduced and connected to this, for example, cohesively.

In 14 is the pivoting element 1 according to 12 shown in section, in which case the threaded nut 24 it can be seen which on the threaded shaft 23 the bolt 22 screwed so that the counter-attack 14 of the bearing element 10 by means of the resulting tensile force 17 against the mounting stop 13 of the holding element 5 is pressed. Again, the touching contact by Montieranschlag 13 and counter-attack 14 close to the second axial stop 9 educated.

In 15 is a belt drive 4 shown in a gearbox 35 is arranged. This is at a transmission input shaft 30 a first cone pulley pair 31 and at a transmission output shaft 33 a second cone pulley pair 32 arranged. At the first cone pulley pair 31 is a first circle of influence 55 with a first running radius 57 set, and on the second cone pulley pair 32 is a second active circle 56 With a second running radius 58 set. A belt 34 runs, here for example in the running direction 54 , on the first circle of effect 55 and the second active circle 56 and transmits so a torque from the transmission input shaft 30 on the transmission output shaft 33 with a gear ratio corresponding to the ratio of the first circle of action 55 to the second circle of activity 56 , The illustrated direction 54 corresponds to an input torque via the transmission input shaft 30 and an embodiment of the belt drive 4 as a traction mechanism. At torque input via the transmission input shaft 30 and execution of the belt 34 as thrust belt is the direction of travel 54 vice versa, but the upper strand (here) remains the Lasttrum 59 , For damping vibrations of the belt 34 is at the load door 59 a damper device 3 provided, which on a pivot bearing 1 about a pivot line across the direction 54 according to the set active circuits 55 and 56 is pivotally mounted. As can be seen, the damper device 3 also translational, namely transversely to the formed Umschlingkreis of the belt 34 , movable. This is a movement of the damper device 3 from a superposition of the pure circular path around the pivot axis 2 following pivotal movement and one to the pivot axis 2 translational movement allows. The result describes the damper device 3 a circular path around one of the pivot axis 2 deviating swing line or an oval (steeper) curve. In the example shown, the empty strand 60 not steamed.

In 16 is a powertrain 29 in a motor vehicle 38 with its motor axis 43 transverse to the longitudinal axis 42 in front of the driver's cab 41 arranged. Here is the belt drive 4 on the input side with the output shaft 37 a drive unit to 36 connected. On the output side is the belt drive 4 connected to a purely schematically illustrated output, so here is a left drive wheel 39 and a right drive wheel 40 with a torque from the drive unit 36 supplied with variable translation. The drive unit 36 is shown here purely by way of example as a three-cylinder internal combustion engine.

Despite the bipartite, the pivoting element proposed here makes possible a very good use of space for a stiff damper device.

LIST OF REFERENCE NUMBERS

1

pivoting element

2

swivel axis

3

damper device

4

wrap-around

5

retaining element

6

first housing element

7

second housing element

8th

first axial stop

9

second axial stop

10

bearing element

11

axial distance

12

end play

13

Montieranschlag

14

counterstop

15

spring element

16

spring force

17

traction

18

rivet

19

Schraubgewindepaarung

20

flange

21

snap

22

bolt

23

threaded shaft

24

threaded nut

25

axial member

26

bearing seat

27

extension

28

twist

29

powertrain

30

Transmission input shaft

31

first conical disk pair

32

second cone pulley pair

33

Transmission output shaft

34

endless

35

gearbox

36

power unit

37

output shaft

38

motor vehicle

39

left drive wheel

40

right drive wheel

41

cab

42

longitudinal axis

43

motor axis

44

conventional assembly game

45

retaining tab

46

conventional pivoting element

47

conventional bearing element

48

conventional mounting stop

49

conventional counter-attack

50

spacer

51

oil pressure

52

opening

53

Draw bolt (blind)

54

direction

55

first circle of action

56

second circle of action

57

first running radius

58

second running radius

59

load strand

60

loose side

61

threaded receptacle

62

screw

63

radial bearings

64

spring pin

65

pin member

66

shell

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been 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.

Cited patent literature

• DE 10017005 A1 [0004]

Claims (8)

Pivoting element (1) for pivotably receiving a damper device (3) of a belt transmission (4), comprising at least the following components: - a holding element (5) which is connectable to a housing element (6) of a belt transmission (4), wherein the retaining element ( 5) has a first axial stop (8); - A bearing element (10) which is axially feasible connected to the holding element (5), wherein the bearing element (10) has a second axial stop (9), wherein the first axial stop (8) and the second axial stop (9) has a predetermined axial distance (11) to each other, so that a damper device (3) with a predetermined axial clearance (12) between the two axial stops (8,9) is axially storable, characterized in that the holding element (5) has a mounting stop (13) and the bearing element ( 10) has a corresponding counter-abutment (14), wherein the mounting stop (13) and the counter-stop (14) are held in contact in the mounted in a Umschlingungsgetriebe (4) in contact, in such a manner that the predetermined axial distance (11) is set , Swivel element (1) to Claim 1 , wherein the bearing element (10) by means of a spring element (15) with a spring force (16) against a housing element (7) is axially supportable, so mounted in a Umschlingungsgetriebe (4) state of the mounting stop (13) and the counter-stop (14) held in touching contact by means of the spring force (16). Swivel element (1) to Claim 1 , wherein the bearing element (10) by means of a tensile force (17) axially acting traction means (18,19,20,21) with the holding element (5) is connected such that the mounting stop (13) and the counter-stop (14) by means of the traction force (17) are held in touching contact, wherein preferably the traction means (18, 19, 20, 21) is formed by means of one of the following components: a rivet (18), preferably a blind rivet; - A screw thread pairing (19); - one after application of the bearing element (10) on the holding element (5) cold-formed flange (20); - An axially acting positive connection, preferably a snap connection (21). Swivel element (1) to Claim 3 in which the traction means (19) is formed by means of a bolt (22) fastened to the holding element (5) with a threaded shank (23) and a threaded nut (24), wherein the threaded nut (24) acts against the counterstop (14) on the rear side, so that the counter-stop (14) is pressed against the Montieranschlag (13). Pivoting element (1) according to one of the preceding claims, wherein the bearing element (10) has an axial element (25) in one piece with the second axial stop (9), wherein the axial element (25) has a bearing seat (26) with a predetermined axial distance (11). corresponding axial extension (27) for a damper device (3), wherein preferably the second axial stop (9) relative to the first axial stop (8) by means of one of the axial element (25) and the holding element (5), particularly preferably the first axial stop (8), anti-rotation lock (28) is secured against relative rotation about the pivot axis (2). A belt transmission (4) for a drive train (29), comprising at least the following components: - A transmission input shaft (30) with a first cone pulley pair (31); - A transmission output shaft (33) with a second cone pulley pair (32); - An Umschlingungsmittel (34), by means of which the first conical disk pair (31) with the second conical disk pair (32) with a variable transmission torque-transmitting connected; - A damper device (3), wherein the damper device (3) for damping the Umschlingungsmittels (34) at least on one side abuts transversely on the Umschlingungsmittel (34); - A transmission housing (35) comprising at least a first housing member (6,7), wherein the transmission housing (35) the conical disk pairs (31,32), the Umschlingungsmittel (34) and the damper device (3) einhaust; and - A pivoting element (1) according to one of the preceding claims for the damper device (3), wherein the pivoting element (1) on the first housing element (6) is fixed such that the damper device (3) on the belt means (34) adjacent and on the pivoting element (1) is pivotally mounted. Drive train (29), comprising a drive unit (36) with an output shaft (37), at least one consumer (39,40) and a belt transmission (4) after Claim 6 wherein the output shaft (37) for torque transmission by means of the belt drive (4) with the at least one consumer (39,40) is connected to a variable ratio. Motor vehicle (38), comprising at least one drive wheel (39,40), which by means of a drive train (29) to Claim 7 is drivable.

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