DE102017111194B3 - Sliding guide and sliding guide pair for a belt drive - Google Patents

Abstract

The invention relates to a sliding guide (1,2) for a belt transmission (3), wherein a first sliding surface (17,20) for abutment on one of the two strands (7,8) of the belt (6) is provided, wherein the first sliding surface (17,20) is mounted such that the first sliding surface (17,20) by means of the strand (7,8) parallel to the set tangent (15,16) is alignable, characterized in that
The wear is reduced and the efficiency increased by a second sliding surface (18,21) for abutment on the same run (7,8) of the belt (6) as the first sliding surface (17,20) is provided, wherein the second sliding surface ( 17, 20) is mounted such that the second sliding surface (18, 21) can be aligned parallel to the set tangent (15, 16) by means of the run (7, 8), and by means of the run (7, 8) different from the first sliding surface (17,20) is alignable. Furthermore, here a Gleitführungspaar (30) is proposed, which comprises two sliding guides (1,2) of the type described above for the two strands (7,8) of a belt (6).
With a sliding guide according to the above description, a good damping is achieved, wherein at the same time the wear on the belt is reducible. In this case, no increased space is required compared to a conventional belt transmission. Rather, a belt can be dimensioned smaller and thus the belt drive, wherein the same life, or with the same dimensions a longer life is achieved.

Description

The invention relates to a sliding guide, a Gleitführungspaar for a belt transmission and a belt transmission, in particular for a drive train of a motor vehicle.

From the state of the art are known Umschlingungsgetriebe with which at least partially a continuous change of the translation (or reduction) is possible. For this purpose, two conical disk pairs are provided, each having two conical disks. The conical disks are each aligned with their lateral surface facing each other and displaceable along their common axis of rotation relative to each other between a maximum spaced position and a minimally spaced position, usually a conical disk is axially fixed and the other conical disk is axially displaceable. Thus, the distance between the conical disks of a cone pulley pair is adjustable.

Between the conical disks of a conical disk pair, a wedge-shaped gap, also called a disk wedge, is formed, which is variable. By means of a common belt, for example a transmission chain, the two pairs of conical disks are connected to each other to transmit torque. The belt means travels radially outwards in a pair of conical disks when its conical disks are guided toward one another; conversely, the looping means travels radially inwardly in a conical disk pair as the conical disk pairs move away from each other. This movement is carried out in a belt drive on the cone pulley pairs usually exactly opposite, so that the distance between the cone pulley pairs can be kept constant and no deflection mechanism or separate chain tensioning mechanism must be provided for the belt means.

Relative to a first pair of conical disks, a transmission input shaft is rotationally fixed, and a transmission output shaft is rotationally fixed relative to a second pair of conical disks connected in a torque-transmitting manner by means of the belt. Depending on the set distance of the conical disks to each other, in relation to the selected distance of the other cone pulley pair, so that a translation is adjustable.

Such a belt transmission is for example from the DE 100 17 005 A1 or the DE 10 2015 201 882 A1 known. In some applications, the belt transmission is combined with a conventional gearbox with fixed gear ratios, so that a larger transmission spread is achieved with a relatively smaller number of fixed gear ratios.

Because of the non-connection tangential leaving the belt from the formed between the conical disks of a cone pulley pair, wedge-shaped gap, in particular due to a polygonal run of a chain, which results from a (usually) finite pitch of a chain, and other dynamic effects at the inlet and outlet in or out the wedge-shaped gap and as a result of changes in the translation or as a result of rotational irregularities and other vibrations, the belt is made to resonate around the Umschlingungsmittelebene. Parameters of the excited resonance oscillation include the chain rotation speed, the chain tension and the state of wear of the chain. The resonances of the resonant vibrations cause structure-borne noise, which is transmitted by means of the conical disks, shafts, bearings and gearbox housing to possibly further components, for example to components of a motor vehicle, and can be converted into undesired airborne sound.

The Umschlingungsmittelebene (or: resonant vibration level) is the shortest tangential connection of the set active circle of the cone pulley pairs, ie the distance between the wedge stump formed between the conical disks of the wedge, which corresponds to the width of the belt. Thus, the position of the resonant vibration plane is variable with the change of the gear ratio. The resonant oscillation plane generally coincides with the median plane in the direction of travel of the respective run, that is to say of the load run (or train run) or of the slack side of the belt.

In order to reduce these resonant vibrations, slide rails are used in the prior art, which bear against the inner and outer sides of the looping means with the least possible play over as long an extension as possible and thus suppress resonant vibrations and undulations of the looping means. Such slide rails are also for example from the above DE 100 17 005 A1 known.

From the German disclosure documents DE 10 2014 216 096 A1 and DE 10 2013 213 159A1 Guiding devices for a belt wrap of a belt pulley belt transmission are known, which two spaced guide portions, between which the belt is feasible, a web portion for connecting the guide portions and a holding portion for holding the guide means have the conical-pulley The guide device has a modular design with a base module and tread modules.

So far, only one slide with a single and rigid sliding surface are considered per run, which is pressed by a spring against the belt. This single sliding surface is designed so stiff that it can not adapt to the chain bend. It was determined on this side that for some operating points a poor efficiency and high wear on the sliding guides or on the chain are generated.

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.

• - eine erste Gleitfläche zum Anliegen an einem der beiden Trume des Umschlingungsmittels, wobei die erste Gleitfläche derart gelagert ist, dass die erste Gleitfläche mittels des Trums parallel zur eingestellten Tangente ausrichtbar ist.

The invention relates to a sliding guide for a belt transmission, wherein the belt transmission comprises a first cone pulley pair and a second cone pulley pair, wherein the conical pulley pairs are connected by means of a belt with a first strand and with a second strand torque transmitting, each conical pulley pair has two conical disks, wherein the two conical disks of a conical disk pair face each other on the lateral surface and have an adjustable distance from each other, wherein the first strand and the second strand of the belt are stretched along a corresponding tangent depending on the set distance, and wherein the sliding guide has at least the following component:

• - A first sliding surface for abutment with one of the two strands of the belt, wherein the first sliding surface is mounted such that the first sliding surface by means of the run parallel to the set tangent is aligned.

The sliding guide proposed here is characterized in that a second sliding surface is provided for abutment with the same strand of the belt as the first sliding surface, wherein the second sliding surface is mounted such that the second sliding surface is aligned parallel to the set tangent means of the strand, and by means of the strand is aligned differently from the first sliding surface.

The sliding guide described herein has the functions and properties known in the art with respect to the choice of material and with respect to the appropriate surface, for example to produce a desired low friction. The belt transmission is also a belt transmission according to the prior art with a first cone pulley pair and a second cone pulley pair as they are known for example from the aforementioned documents. Also known is the coordination of the spacing of the respective conical disks of a pair of conical disks and the tension of the belt or the first strand, for example the load strand, and the second strand, for example the slack side, of the prior art. As a result of the set distance thus results in a tangent or the shortest tangential connection of the set active circuits, as described above. The sliding guide now has a first sliding surface, which is designed to abut against one of the two strands, specifically that of the associated sliding guide, in order thus to reduce or prevent deflection of the belt as a result of induced resonance vibrations. For this purpose, the first sliding surface is mounted such that the first sliding surface is aligned parallel to the set tangent, passively through the associated strand itself.

For many applications, the first sliding surface also has a clamping means by means of which the first sliding surface is pressed against the strand and thus tensions the strand. A tensioning means is for example a spring, for example a helical spring, whose clamping force is aligned perpendicular to the sliding surface. Alternatively, the clamping means is formed for example as a solid-state spring, as for example from the DE 10 2015 201 882 A1 is known. Also in this embodiment, the clamping force is aligned at least in an orientation of the associated sliding surface perpendicular to the associated sliding surface.

Now, furthermore, it is proposed here to provide a second sliding surface which, like the first sliding surface, is designed to abut against the same strand of the belting means on which the first sliding surface also bears. The second sliding surface is in this case mounted identically as the first sliding surface, so that the second sliding surface is set up to damp or suppress a deflection of the belt or the strand due to induced resonance vibrations. Here, however, the first sliding surface and the second sliding surface stored independently of each other so that they can assume different orientations. If, for example, a simple resonance oscillation belly, that is to say a resonance oscillation of the first order, is present, then the first and second sliding surfaces can be arranged at an angle to each other, deviating from a parallel assignment to each other and the desired tangent, so that they have, for example, a V-shape form. As a result, the number of abutment points of the sliding surfaces compared to a single, rigid sliding surface is doubled, so that at the same clamping force the punctual surface load is halved to the assigned run or the edges of the sliding surfaces.

In a particularly preferred embodiment, the first sliding surface and the second sliding surface are arranged to each other such that at a second order resonant vibration of the associated strand, so where two Resonanzschwingungsbäuche are formed, the first sliding surface approximately centrally to the first resonance vibration belly and the second sliding surface approximately centrally to second resonant vibration belly are arranged. In such an arrangement, it is a possible state that the first sliding surface and the second sliding surface to each other, and preferably to the target tangent, on the one hand aligned in parallel, and are arranged simultaneously in mutually offset planes.

It should be noted that the definition of the sliding surfaces selected here also includes the counter-sliding surface described below. Preferably, two sliding surfaces of a sliding guide are arranged on the same side to the associated strand, particularly preferably on the inside of the belt, because this arrangement is particularly space-saving. The inner side or the inner side is here the space enclosed by the belt, through which the waves of the conical pulley pairs extend. The outer side or the outer side is correspondingly referred to as the space which, viewed from the inside, is arranged beyond the belting means, ie towards a transmission housing.

In a further advantageous embodiment of the sliding guide, the first sliding surface and the second sliding surface are alignable by means of a common bearing parallel to the set tangent of the associated strand.

In this preferred embodiment, the first and second sliding surfaces are supported by means of a common bearing, so that no additional bearing must be provided. Particularly preferably, the first sliding surface and the second sliding surface are mounted on a conventional bearing, which is set up for a simple sliding guide.

In a further advantageous embodiment of the sliding guide, the first sliding surface and the second sliding surface can be prestressed against the associated strand by means of a common tensioning means.

According to this advantageous embodiment, the first sliding surface and the second sliding surface by means of a common clamping means against the associated strand can be prestressed, wherein preferably a conventional tensioning means is used. Such a conventional tensioning means is known, for example, from the documents cited above.

Here, according to one embodiment, an intermediate element is provided, to which the first sliding surface and the second sliding surface are tiltable and / or displaceably mounted. Preferably, in this case, the intermediate element by means of the common clamping means on the common bearing, as described above, stored and biased.

In a further advantageous embodiment of the sliding guide, the first sliding surface and the second sliding surface can be prestressed against the associated strand by means of two separate tensioning means.

According to an alternative embodiment, the first sliding surface and the second sliding surface can each be prestressed against the associated strand by means of a separate tensioning means. In this case, no further intermediate element is particularly preferably provided. In a particularly preferred embodiment, the first sliding surface and the second sliding surface are supported via a common bearing as described above, preferably a conventional bearing.

In a further advantageous embodiment of the sliding guide, the first sliding surface and the second sliding surface are connected in series in the direction of the associated run.

In this advantageous embodiment, the first sliding surface and the second mating surface in the direction of the associated strand in series, ie parallel to the desired tangent connected. This achieves a simple embodiment for adapting the sliding surfaces to the resonance mode of the associated run. In one embodiment, the first sliding surface and the second sliding surface are connected to each other via a common bearing. In another embodiment, a further member between the two sliding surfaces is provided, so that in addition to a tilt relative to each other also a (for example, parallel) offset of the sliding surfaces to each other is possible.

In a further advantageous embodiment of the sliding guide, at least one further sliding surface is provided, which is mounted such that the further sliding surface can be aligned parallel to its set tangent by means of the associated run and can be aligned differently from the first sliding surface and / or second sliding surface by means of the associated run is.

In this advantageous embodiment, a third sliding surface or even a fourth sliding surface or even more sliding surfaces is provided, which is differently oriented to at least one of the other sliding surfaces. The individual sliding surfaces are either all or partially connected as described above in series or all but separately, preferably by means of an intermediate element, aligned over different camps or a common camp parallel to Trum. Each sliding surface may have its own clamping means or several or all sliding surfaces a common clamping means. With each additional sliding surface, the number of abutment points is increased at a resonance oscillation of the assigned run, so that the punctual surface load decreases with the same contact pressure resulting from the pretension.

In a further advantageous embodiment of the sliding guide is at least one mating sliding surface, preferably a number of sliding surfaces identical number of Gegengleitflächen provided, wherein the at least one Gegengleitfläche is arranged for abutment on the same strand on the opposite sides of the sliding surfaces and parallel to the set tangent can be aligned , and preferably by means of the strand is different from at least one of the sliding surfaces aligned.

According to this advantageous embodiment, at least one counter sliding surface is provided, which is arranged opposite the sliding surfaces on the associated strand. If, for example, a sliding surface is arranged on the inside of the belting means relative to the belting means, then the counter sliding surface is arranged on the outside, or vice versa. The mating sliding surface can be aligned parallel to the set tangent and can be aligned differently to at least one of the two sliding surfaces or a plurality of sliding surfaces.

In one embodiment, the mating sliding surface is fixedly connected to one of the sliding surfaces so that the orientation of the mating sliding surface offset by approximately the radial width of the strand is identical to the connected sliding surface. In a preferred embodiment, each of the sliding surfaces has a fixedly connected counter sliding surface, which thus in each case has the same (parallel offset) orientation as the associated sliding surface.

In an alternative embodiment or in addition to the described embodiment, the sliding guide has at least one counter sliding surface, which can be aligned differently relative to the sliding surfaces. Particularly preferably, such an independent counter sliding surface, as described above, connected in series with the sliding surfaces. Such an independent counter sliding surface is particularly preferably pretensioned by a tensioning means or the / the clamping means of the sliding surfaces against the associated strand. Alternatively, the mating sliding surface has its own tensioning means.

According to a further aspect of the invention, a Gleitführungspaar for a belt transmission is proposed, wherein the Gleitführungspaar comprises a first sliding guide according to an embodiment according to the above description for the first strand and a second sliding guide according to one embodiment according to the above description for the second strand Sliding guides are aligned to the respective tangent of the respective assigned strand and can be biased against the respective assigned strand, preferably by means of a common bearing and / or preferably by means of a common clamping means.

Furthermore, a Gleitführungspaar is proposed here, which comprises two sliding guides of the type described above for the two strands of a belt. According to this aspect of the invention, a Gleitführungspaar is proposed which is provided with a first sliding guide on a first strand, for example on the load strand, and a second sliding guide for the second strand, for example on the back strand. Preferably, a belt transmission in assembly only a single pair of sliding guide, wherein the number of sliding surfaces of the two sliding guides of Gleitführungspaars need not necessarily be identical. In particular, in an embodiment in which the first strand is always the Lasttrum and the second strand is always the slack side, or vice versa, the requirements for a sliding guide for each Trum may be different. Here, the use of a Gleitführungspaars recommended with different each adapted to the occurring resonant vibrations different sliding guides with possibly a different number and arrangement of sliding and Gegeng leitflächen.

Each strand of the belt forms its own tangent, which are parallel to each other only when set, the same circle of action on the conical disk pairs, ie a ratio of the factor one, and otherwise inclined to each other for trapezoidal smaller circle of action. The resonance vibrations, which the respective strand can thereby be different at the same time, so that particularly preferably the two sliding guides are independently biased against the respectively assigned strand. Even in one embodiment with a common bearing for both sliding guides, the sliding guides are preferably each independently alignable on the common bearing.

In one embodiment, in which a common tensioning means is provided, the bearing is set up such that the sliding guides can be aligned independently of one another by means of the respective assigned run.

• - zumindest eine Getriebeeingangswelle mit einem ersten Kegelscheibenpaar;
• - zumindest eine Getriebeausgangswelle mit einem zweiten Kegelscheibenpaar;
• - zumindest ein Umschlingungsmittel, welches das erste Kegelscheibenpaar mit dem zweiten Kegelscheibenpaar drehmomentübertragend verbindet;
• - zumindest eine Gleitführung nach einer Ausführungsform gemäß der obigen

According to a further aspect of the invention, a belt drive for a drive train is proposed, wherein the belt transmission has at least the following components:

• - At least one transmission input shaft with a first cone pulley pair;
• - At least one transmission output shaft with a second cone pulley pair;
• - At least one Umschlingungsmittel, which connects the first conical disk pair with the second conical disk pair to transmit torque;
• - At least one sliding guide according to an embodiment according to the above

Description or a Gleitführungspaar according to the above description, wherein the at least one sliding guide for damping the at least one wrapping means biased against the respective associated strand.

With the belt transmission proposed here, a torque is translatable or reducible transferable, the transmission is at least partially infinitely adjustable. The translation is set via the two conical disk pairs, as described above. The belt is arranged between the respective relatively movable conical pulley pairs and transmits a torque from a cone pulley pair on the other cone pulley pair. Preferably, the belt is held at a constant length. The at least one sliding guide, preferably the two sliding guides of the above-described sliding guide pair, is (are) aligned parallel to the belt, wherein the individual sliding surfaces are passive to the resonance vibration belly at a first order resonance vibration or the resonance vibration bellies at a higher order resonance vibration, ie by means of of the respective assigned run, are adaptable in the orientation. As a result, the surface load is reduced due to the bias. The wear on the respective sliding guide and / or the belt is reduced and increases the efficiency of torque transmission.

According to a further aspect of the invention, a drive train having a drive unit with an output shaft, at least one consumer and a belt transmission as described above is proposed, 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 output shaft for use as needed, ie taking into account the required rotational speed and the required torque. The use is, for example, an electric generator for providing electrical energy. In order to selectively transmit the torque and / or by means of a gearbox with different ratios, the use of the belt transmission described above is particularly advantageous because a large spread in a small space is achievable. 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 suitably arranged torque transmission line. Furthermore, in a preferred embodiment, a plurality of drive units are provided, which are operable in series or in parallel or decoupled from one another and whose torque can be made available as needed by means of a belt transmission according to the above description. Examples are hybrid drives of electric motor and internal combustion engine, but also multi-cylinder engines in which individual cylinders (groups) are switchable. With the belt transmission proposed here, a torque transmission with increased efficiency at the same time increased life, at least of the belt, and thus extended maintenance intervals or even a loss of maintenance over the desired life of the drive train is possible. Alternatively or additionally, more favorable materials and / or a reduction of the (rotating) masses can be achieved, whereby a further increase in the efficiency can be achieved.

According to a further aspect of the invention, a motor vehicle is proposed which has at least one drive wheel, wherein the drive wheel can be driven by means of a drive train as described above.

Most motor vehicles today have a front-wheel drive and sometimes arrange the drive unit, for example an internal combustion engine 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. The drive train described above has a belt drive of small size, with high efficiency and long maintenance intervals can be achieved. This is achieved by means of the sliding guide or Gleitführungspaars proposed here with the segmented sliding surfaces, by means of which a small punctual surface load can be achieved in induced in the belt means resonant vibrations.

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 Ka + or Renault Clio.

• 1: schematisch ein Umschlingungsgetriebe, wobei das erste Trum schematisch am oberen Totpunkt einer Resonanzschwingung 1. Ordnung dargestellt ist;
• 2: schematisch ein Umschlingungsgetriebe, wobei das erste Trum schematisch am ersten Totpunkt einer Resonanzschwingung 2. Ordnung dargestellt ist;
• 3: eine einfache Gleitführung anliegend an einem Umschlingungsmittel, welches sich im oberen Totpunkt einer Resonanzschwingung 1. Ordnung befindet;
• 4: eine einfache Gleitführung anliegend an einem Umschlingungsmittel, welches sich im unteren Totpunkt einer Resonanzschwingung 1. Ordnung befindet;
• 5: eine Gleitführung mit zwei Gleitflächen, welche am Trum anliegen, welches sich im oberen Totpunkt einer Resonanzschwingung 1. Ordnung befindet;
• 6: eine Gleitführung mit zwei Gleitflächen, welche am Trum anliegen, welches sich im unteren Totpunkt einer Resonanzschwingung 1. Ordnung befindet;
• 7: schematisch ein Umschlingungsgetriebe mit einem Gleitführungspaar, wobei die erste Gleitführung drei Gleitflächen und die zweite Gleitführung zwei Gleitflächen aufweist;
• 8: schematisch ein Umschlingungsgetriebe mit einem Gleitführungspaar, wobei die Gleitführungen jeweils Gegenflächen aufweisen;
• 9: schematisch ein Umschlingungsgetriebe in Ansicht von oben, wobei die zweite Gleitführung zu erkennen ist; und
• 10: 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 schematically a belt drive, wherein the first strand is shown schematically at the top dead center of a resonant vibration of the first order;
• 2 schematically a belt drive, wherein the first strand is shown schematically at the first dead center of a second order resonance oscillation;
• 3 : a simple sliding guide adjacent to a belt, which is at the top dead center of a 1st order resonance vibration;
• 4 : a simple sliding guide adjacent to a belt, which is in the bottom dead center of a 1st order resonance vibration;
• 5 : a sliding guide with two sliding surfaces, which bear against the run, which is at the top dead center of a 1st order resonance vibration;
• 6 : a sliding guide with two sliding surfaces, which abut the strand, which is in the bottom dead center of a resonance vibration of the 1st order;
• 7 schematically a belt drive with a Gleitführungspaar, wherein the first sliding guide has three sliding surfaces and the second sliding guide has two sliding surfaces;
• 8th schematically a belt transmission with a Gleitführungspaar, wherein the sliding guides each have opposing surfaces;
• 9 schematically a belt drive in top view, wherein the second sliding guide can be seen; and
• 10 : a drive train in a motor vehicle with belt drive.

In the following, ordinal numbers are used for the sliding guides, sliding surfaces, conical disk pairs, strands and other elements. These serve only the clear distinctness and do not justify any order, ranking and does not have to mean that another similar element is necessarily provided, unless otherwise explicitly defined in the individual case.

In 1 is schematically a belt transmission 3 shown, which has a first cone pulley pair 4 (here in the illustration on the left) and a second cone pulley pair 5, wherein the two conical pulley pairs 4 and 5 by means of a belt 6 are connected torque transmitting. The wrapping means 6 forms a first strand 7 (here in the illustration above), here for example the Lasttrum, and a second Trum 8th , here for example the empty strand. Due to the set distance of the respective conical disks of the conical disk pairs 4 and 5, the first tangent result 15 and the second tangent 16, along which the first strand 7 or the second strand 8th ideally run. The tangents 15 and 16 are shown with arrow direction in an exemplary direction. For details will be on 9 and the disclosure in the prior art. In 1 is further shown that the first strand 7 in resonance vibration 1 , Order is swinging. This is shown by the dashed representation of the top dead center of the resonant oscillation, which is from the ideal tangent 15 differs. This resonant oscillation is decisively excited by the polygonal clearance in a chain-like belt. The parameters for the occurrence of a resonance vibration include the rotational speed of the belt, the tensile force in the belt, the state of wear of the belt.

In 2 is a belt drive 3 in the same state as in 1 shown, here is the first strand 7 at the first dead center of a resonance oscillation 2 , Order is.

In 3 is a simple sliding guide 45 adjacent to a first strand 7 a belt 6, wherein the first strand 7 at the top dead center of the resonance oscillation 1 , Order is. The first run 7 is stretched by the Trumspannkraft 44 and is so on the local friction points 47 the individual sliding surface 46 the simple sliding guide 45 pressed. The sliding surface 46 is by means of a clamping device 43 perpendicular to the strand 7 biased and is around the camp 22 tiltable.

In 4 is the same construction as in 3 shown, here is the first strand 7 in the bottom dead center of the resonance oscillation 1 , Order is. Here, there is only a single point of contact, which is the local friction points 47 forms. The 3 and 4 It can be seen that the local riding load on the belt 6 is high due to the small number of local friction points.

In 5 is the same state of the belt 6 as in 3 shown, with a sliding guide here 1 is provided, which a first sliding surface 17 and a second sliding surface 18 having. The first sliding surface 17 and the second sliding surface 18 are about a common camp 22 and a common clamping device 23 tilted biased. The first sliding surface 17 and the second sliding surface 18 are passive by the present deflection of the strand 7 aligned differently to each other. This will set the number of local friction points 47 compared to the structure of a simple sliding guide 46 (see 3 ) doubled.

In 6 is the same construction as in 5 shown, here is the first strand 7 in the bottom dead center of the resonance oscillation 1 , Order is (compare also 4 ). Again, the number of local friction points 47 compared to a simple sliding guide 46 doubled.

In 7 is a belt drive 3 shown schematically, in which, as in 1 and 2 shown, a first cone pulley pair 4 and a second pair of conical disks 5 are provided, which are connected to one another by torque transmission means of a belt 6. The belt 6 forms thereby a first Trum 7 from, on which a first sliding guide 1 is present and a second strand 8th at which a second sliding guide 2 is applied. These together form a Gleitführungspaar 30 , The first sliding guide 1 and the second sliding guide 2 can be identical or even, as shown, different. The first sliding guide 1 has a first sliding surface 17 , a second sliding surface 18 and another sliding surfaces 19 on. These are each about a common clamping device 23 on a common camp 22 biased against the first strand 7 tilted stored. Here are for each of the sliding guides 1 and 2 a separate warehouse 22 provided because thereby by means of a little expensive construction, the cone pulley pairs 4 and 5 can be arranged very close to each other.

The first sliding surface 17 , the second sliding surface 18 and the other sliding surface 19 are each different from each other aligned, and thus can be a resonance waveform of the first strand 7 adapt so that the number of local friction points 47 compared to a simple sliding guide 46 (see 3 . 4 . 5 and 6 ) are multipled, in this case tripled.

The second sliding guide 2 is formed in an alternative embodiment, in which case a fourth sliding surface 20 and a fifth sliding surface 21 are provided, which by means of a first separate clamping means 24 and a second separate clamping means 25 on a common bearing 22 biased against the second strand 8 are mounted tilted. Here are the fourth sliding surface 20 and the fifth sliding surface 21 connected in series with each other, so that the fourth sliding surface 20 and the fifth sliding surface 21 are aligned differently with each other, but compared to the embodiment of the first sliding guide 1 on the first run 7 one of which can perform different relative movement to each other.

In 8th is a similar embodiment of a belt drive 3 with a sliding guide pair 30 as in 7 shown. Here, the sliding guides 1 and 2 respectively Gegengleitflächen26 to 29, which on the outer circumference of the belt 6 issue. This has the advantage that very good damping properties can be achieved. In the following, only the differences from the embodiment in 7 received.

The first sliding guide 1 points to the first sliding surface 17 a first counter sliding surface 26 on, and to the second sliding surface 18 a second counter sliding surface 27 and to the other sliding surface 19, a further counter sliding surface 28 on. The counter-gliding surfaces 26 to 28 are each to their associated sliding surface 17 to 19 fixed, so rigidly aligned. It follows that the first mating surface 26 is always aligned parallel to the first sliding surface 17, and this also for the second Gegengleitfläche 27 based on the second sliding surface 18 and the other mating surface 28 related to the further sliding surface 19 applies. However, this is not a condition for the specific embodiment. Furthermore, regardless of here is a single centrally located common clamping device 23 provided so that in comparison to the embodiment in 7 when tilting a lower compared to restoring torque is applied.

Regarding the second sliding guide 2 are the first sliding surface 20 and the second sliding surface 21 and its bias and bearing identical to the embodiment in FIG 7 , Furthermore, a completely independent Gegengleitfläche 29 is provided which via another separate clamping means 48 against the second run 8th biased and tiltable about the common camp 22 is stored. The counter-gliding surface 29 the second sliding guide 2 can thus be completely independent of the first sliding surface 20 and also completely independent of the second sliding surface 21 move.

In 9 is a belt drive 3 shown in plan view, wherein the wrapping means 6 is cut and a second sliding guide 2 only schematically with a fourth sliding surface 20 and a fifth sliding surface 21 which is indicated on the second strand 8th rest on top in this illustration. The belt transmission 3 has a first cone pulley pair 4 with a first conical disk 9 and a second conical disk 10 and a second cone pulley pair 5 with a third cone pulley 11 and a fourth cone pulley 12 on. The conical disks 9 . 10 or 11,12 of a respective cone pulley pair 4 and 5 are adjustable to each other spaced. Here is the first cone pulley pair 4 a first distance 13 set which is smaller than a corresponding second distance 14 of the second cone pulley pair 5. This is the belt 6 on the first conical disk pair 4 on a larger first radius of revolution 49 guided as the corresponding second orbital radius 50 of the second cone pulley pair 5 , This is a translation of the transmission of torque from the transmission input shaft 32 to the transmission output shaft 33 or vice versa between a minimum radius of rotation and a maximum radius of rotation for the belt 6 freely adjustable.

In 10 is a powertrain 31 comprising a drive unit 34 , shown here as an internal combustion engine, and an output shaft 35 , a belt transmission 3 and a torque transmitting connected, left drive wheel 39 and right drive wheel 40 , shown schematically. The left drive wheel 39 forms, for example, a first consumer 36 and the second drive wheel 40, a second consumer 37 wherein a consumer may also be formed by (not shown) an accumulator for recuperation of the braking energy or an air conditioner and further. The powertrain 31 is arranged here in a motor vehicle 38, wherein the drive unit 34 with its motor axis 43 transverse to the longitudinal axis 42 in front of the driver's cab 41 is arranged.

With a sliding guide according to the above description, a good damping is achieved, wherein at the same time the wear on the belt is reducible. In this case, no increased space is required compared to a conventional belt transmission. Rather, a belt can be dimensioned smaller and thus the belt drive, wherein the same life, or with the same dimensions a longer life is achieved.

LIST OF REFERENCE NUMBERS

1

first sliding guide

2

second sliding guide

3

wrap-around

4

first conical disk pair

5

second cone pulley pair

6

endless

7

first run

8th

second run

9

first cone pulley

10

second cone pulley

11

third cone pulley

12

fourth cone pulley

13

first distance

14

second distance

15

first tangent

16

second tangent

17

first sliding surface (the first sliding guide)

18

second sliding surface (the first sliding guide)

19

additional sliding surface (the first sliding guide)

20

fourth sliding surface (first sliding surface of the second sliding guide)

21

fifth sliding surface (second sliding surface of the second sliding guide)

22

common camp

23

common clamping device

24

first separate clamping device

25

second separate clamping device

26

first counter sliding surface (the first sliding guide)

27

second counter sliding surface (the first sliding guide)

28

additional counter sliding surface (the first sliding guide)

29

fourth counter sliding surface (counter sliding surface of the second sliding guide)

30

Gleitführungspaar

31

powertrain

32

Transmission input shaft

33

Transmission output shaft

34

power unit

35

output shaft

36

first consumer

37

second consumer

38

motor vehicle

39

left drive wheel

40

right drive wheel

41

cab

42

longitudinal axis

43

motor axis

44

Trumspannkraft

45

simple sliding guide

46

single sliding surface

47

local friction point

48

another separate clamping device

49

first radius of revolution

50

second radius of revolution

Claims (10)

Sliding guide (1,2) for a belt transmission (3), wherein the belt transmission (3) has a first cone pulley pair (4) and a second cone pulley pair (5), wherein the conical pulley pairs (4,5) by means of a belt (6) with a first strand (7) and with a second strand (8) are connected to transmit torque, wherein each conical disk pair (4,5) two conical disks (9,10,11,12), wherein the two conical disks (9,10,11, 12) of a pair of conical disks (4, 5) face each other on the lateral surface and have an adjustable distance (13, 14) relative to one another and the first run (7) and the second run (8) of the belt (6) depend on the set distance (13 , 14) are respectively stretched along a corresponding tangent (15, 16), and wherein the sliding guide (1, 2) comprises at least the following component: a first sliding surface (17, 20) for abutment against one of the two strands (7, 8) ) of the belt (6), wherein the first sliding surface (17, 20) is mounted such that the first sliding surface (17, 20) can be aligned parallel to the set tangent (15, 16) by means of the run (7, 8), characterized in that a second sliding surface (18, 21) for abutment with the same run (7,8) of the belt (6) as the first sliding surface (17,20) is provided, wherein the second sliding surface (17,20) is mounted such that the second sliding surface (18,21 ) is aligned parallel to the set tangent (15,16) by means of the run (7,8), and by means of the run (7,8) is different from the first sliding surface (17,20) alignable. Sliding guide (1,2) to Claim 1 , wherein the first sliding surface (17, 20) and the second sliding surface (18, 21) can be aligned parallel to the set tangent (15, 16) of the associated run (7, 8) by means of a common bearing (22). Sliding guide (1,2) to Claim 1 or 2 , wherein the first sliding surface (17) and the second sliding surface (18) by means of a common clamping means (23) against the associated strand (7) are prestressed. Sliding guide (1,2) to Claim 1 or 2 , wherein the first sliding surface (20) and the second sliding surface (21) by means of two separate clamping means (24,25) against the associated strand (8) are prestressed. Sliding guide (1,2) to Claim 4 wherein the first sliding surface (20) and the second sliding surface (21) in the direction of the associated run (8) are connected in series with each other. Sliding guide (1,2) according to one of the preceding claims, wherein at least one further sliding surface (19) is provided, which is mounted such that the further sliding surface (19) by means of the associated run (7) parallel to its set tangent (15) is alignable, and by means of the associated run (7) different from the first sliding surface (17) and / or second sliding surface (18) is alignable. Sliding guide (1,2) according to one of the preceding claims, wherein at least one mating sliding surface (27,28,29), preferably one to the number of sliding surfaces (17,18,19) identical number of Gegengleitflächen (27,28,29) provided is, wherein the at least one mating sliding surface (27,28,29) for abutment on the same strand (7,8) on the sliding surfaces (17,18,19,20,21) opposite side is arranged and parallel to the set tangent (15 , 16), and preferably by means of the run (8) is different from at least one of the sliding surfaces (20,21) is alignable. Sliding guide pair (30) for a belt transmission (3), comprising a first sliding guide (1) according to one of the preceding claims for the first run (7) and a second sliding guide (2) according to one of the preceding claims for the second run (8), wherein the sliding guides (1, 2) can be aligned with the respective tangent (15, 16) of the respectively assigned run (7, 8) and can be prestressed against the respectively assigned run (7), preferably by means of a common bearing (22) and / or preferably by means of a common tensioning means (23). A belt transmission (3) for a drive train (31), comprising at least the following components: - at least one transmission input shaft (32) with a second pair of conical disks (5); - At least one transmission output shaft (33) with a first cone pulley pair (4); - At least one Umschlingungsmittel (6), which connects the first cone pulley pair (4) with the second cone pulley pair (5) to transmit torque; - At least one sliding guide (1,2) according to one of Claims 1 to 7 or a Gleitführungspaar (30) after Claim 8 , wherein the at least one sliding guide (1,2) for damping the at least one belt means (6) biased against the respective associated strand (7,8). Drive train (31) comprising a drive unit (34) with an output shaft (35), at least one consumer (36,37) and a belt transmission (3) according to Claim 9 wherein the output shaft (35) for torque transmission by means of the belt drive (3) with the at least one consumer (36,37) is connected to a variable ratio.

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